Clutch assembly and system

ABSTRACT

Power transmission systems including clutch arrangement and control systems are adapted to be used in numerous different operational environments. Such power transmission systems may include clutch arrangements that provide more effective power transmission capabilities, reduced vibration, greater durability and longer life. Control arrangements are provided to more effectively control and monitor clutch operation in ways that provide for greater system flexibility and drive options. Structures that minimize vibrations may be included in a clutch housing as well as in clutch and separator discs of a disc pack.

TECHNICAL FIELD

This disclosure relates to mechanical power transmission systems.Exemplary embodiments particularly relate to clutch assemblies andsystems in which clutch assemblies are used for selectively transmittingpower.

BACKGROUND

Power transmission systems are used to selectively deliver rotationalpower from a driver device such as an internal combustion engine,electric motor or other source of rotational power, to a driven device.Driven devices may commonly include such things as pumps, electricgenerators, the tires of a vehicle or the propeller of a watercraft.Clutches are used to selectively operatively engage and disengage thedriver from the driven device.

Mechanical clutches commonly operate to selectively engage and disengagethe driver and driven devices by having a stack of adjacent clutchdiscs. The discs in the stack which is also referred to herein as a discpack, are alternatively mechanically operatively engaged with drivingand driven members. The axial force that acts between the discs can beselectively varied. When the clutch is not engaged, the discs that movewith the driving member are sufficiently movable relative to the discsthat are engaged with the driven member such that they can rotaterelative thereto. To engage the clutch, the discs in the stack areaxially compressed such that the discs connected to the driving memberare in pressurized abutting engagement with the discs connected to thedriven member. As a result, the driven member is caused to rotate withthe driving member, and the driven device is engaged with the driver.

High friction material is often attached to the discs to provideenhanced frictional engagement when the clutch is engaged. Releasing theaxial compression force causes the discs to again be able to rotaterelative to one another and the clutch is disengaged. Springs or similarmechanisms can be positioned to act on the discs to facilitate the discssufficiently separating to disengage the clutch when the axialcompression force is released.

Mechanical clutches commonly experience certain types of issues whichlimit their capabilities and useful life. These include wearing of theclutch discs over time with repeated engagement and disengagement of theclutch. Other issues may include providing sufficient axial force to thediscs in order to transmit the level of power needed to operate thedriven device. Other issues include avoiding excessive heat which canshorten the life of clutch discs and also limit power transmissioncapabilities. Other issues include vibration and torsional stresses.Other issues include damage to clutch components when the clutch isoperated in a slipping mode for an extended period of time. Additionalproblems and drawbacks can be encountered with mechanical clutches andsystems depending upon the particular system in which a clutch is used.

Mechanical clutches and related systems may benefit from improvements.

OBJECTS OF EXEMPLARY EMBODIMENTS

It is an object of some exemplary embodiments to provide an improvedmechanical clutch.

It is a further object of some exemplary embodiments to provide animproved mechanical clutch with greater power transmission capabilities.

It is a further object of some exemplary embodiments to provide animproved mechanical clutch with longer life.

It is a further object of some exemplary embodiments to provide animproved mechanical clutch for use in marine applications.

It is a further object of some exemplary embodiments to provide animproved mechanical clutch that is more economical to operate.

It is a further object of some exemplary embodiments to provide animproved mechanical clutch that is lighter in weight.

It is a further object of some exemplary embodiments to provide animproved mechanical clutch that provides for controlled engagement.

It is a further object of some exemplary embodiments to provide animproved mechanical clutch that can operate for extended periods in aslipping mode without adverse consequences.

It is a further object of some exemplary embodiments to provide animproved mechanical clutch that can be used in hybrid drive systems.

It is a further object of some exemplary embodiments to provide animproved mechanical clutch and system that can provide benefits inperformance.

It is a further object of some exemplary embodiments to provide animproved mechanical clutch and system that can be more readily serviced.

It is a further object of some exemplary embodiments to provide methodsof making improved mechanical clutches and systems.

It is a further object of some exemplary embodiments to provide a methodfor repairing mechanical clutches.

Further objects of exemplary embodiments will be made apparent in thefollowing Detailed Description and the appended claims.

The foregoing objects are accomplished by the exemplary embodimentsemploying the principles described herein.

BRIEF DESCRIPTION OF DRAWINGS

FIG. 1 is an isometric schematic view of a ship including clutch systemsof some exemplary embodiments.

FIG. 2 is an isometric view including components of a drive system for aship.

FIG. 3 is an isometric view of an exemplary clutch.

FIG. 4 is a rear view of the clutch shown in FIG. 3.

FIG. 5 is a cross-sectional view of the clutch taken along line 5-5 inFIG. 4.

FIG. 6 is a partial cross-sectional view showing the rotational fluidcoupling connection of the clutch shown in FIG. 5.

FIG. 7 is an enlarged cross-sectional view showing the actuation port ofthe fluid coupling shown in FIG. 6.

FIG. 8 is an enlarged cross-sectional view of the fluid coupling andflow passages of an exemplary arrangement.

FIG. 9 is a rear isometric view of a further alternative embodiment of aclutch adapted to operate for extended periods in a slipping mode.

FIG. 10 is a front isometric view of the clutch shown in FIG. 9.

FIG. 11 is a front plan view of the clutch shown in FIG. 9.

FIG. 12 is a cross-sectional view of the clutch shown in FIG. 9.

FIG. 13 is an enlarged cross-sectional view of the clutch shown in FIG.10.

FIGS. 14-19 show alternative types of grooving in clutch discs which maybe used with the clutch shown in FIG. 9.

FIG. 20 is a plan view of a shaft, clutch disc and serrated Bellevillespring for use in an exemplary clutch such as that shown in FIG. 9.

FIG. 21 is an isometric view of a hub, Belleville spring and clutchdiscs similar to that shown in FIG. 20.

FIG. 22 is a plan view of an exemplary serrated Belleville spring.

FIG. 23 is a side cross-sectional view of a plurality of clutch discsand separator discs where serrated Belleville springs extendintermediate of the separator discs.

FIG. 24 is a schematic view of an exemplary control system for aslipping clutch.

FIG. 25 is a schematic view of a ship including an exemplary hybriddrive system.

FIG. 26 is an exemplary schematic view of an engine room including ahybrid drive system.

FIG. 27 is a rear plan view of an air-cooled clutch of an alternativeexemplary embodiment.

FIG. 28 is a cross-sectional view of the air-cooled clutch taken alongline 28-28 in FIG. 27.

FIG. 29 is a sectional view taken along line 29-29 in FIG. 27.

FIG. 30 is an isometric view of a segment of an exemplary moldedcomposite clutch disc of an exemplary embodiment suitable for use inconnection with the clutch shown in FIG. 27.

FIG. 31 is a cross-sectional view of the composite clutch disc shown inFIG. 30.

FIG. 32 is a rear top isometric view of an alternative embodiment of aclutch housing.

FIG. 33 is a cross-sectional view of the clutch housing shown in FIG. 32and the clutch therein.

FIG. 34 is a cross-sectional view of an exemplary fluid coupling usedfor delivering actuation fluid and cooling fluid to the clutch shown inFIG. 33.

FIG. 35 is an enlarged cross-sectional view of the right side detail ofthe fluid coupling of FIG. 34.

FIG. 36 is an enlarged cross-sectional view of the fluid couplingrepresenting controlled fluid flow axially through a radial gap.

FIG. 37 is a front view of an exemplary vibration damping coupling thatmay be used with clutches of some exemplary embodiments.

FIG. 38 is a diametrical cross-sectional view of the coupling shown inFIG. 37

FIG. 39 is a schematic view of an exemplary control system for operationof a clutch.

FIGS. 40-46 are a schematic representation of exemplary control logiccarried out by an exemplary clutch control system.

FIG. 47 is a partial cross-sectional view of a clutch which includes anexemplary vibration damping arrangement.

FIG. 48 is an inboard end view of the clutch shown in FIG. 47.

FIG. 49 is an exploded view of an inner housing ring and an outerhousing ring of an exemplary disc housing of the type shown in FIG. 47.

FIG. 50 is an outboard end view of the exemplary disc housing shown inthe clutch of FIG. 47.

FIG. 51 is a perspective view of the disc housing shown in FIG. 50.

FIG. 52 is a sectional perspective view of the disc housing shown inFIG. 51.

FIGS. 53 and 54 are exemplary deformable resilient bodies includingblocks that may be used in the disc housing shown in FIG. 50.

FIG. 55 is an enlarged view of a portion of the disc housing of FIG. 50showing the exemplary deformable resilient blocks of FIG. 53.

FIG. 56 is an outboard end view of an alternative drive ring.

FIG. 57 is a perspective view of the alternative drive ring shown inFIG. 56.

FIG. 58 is a perspective section view of the drive ring shown in FIG.57.

FIG. 59 is a perspective view of an alternative deformable resilientbody used in the exemplary drive ring of FIG. 56.

FIG. 60 is a partial cross-sectional view of a clutch similar to theclutch shown in FIG. 47 but including the alternative drive ring of FIG.56.

FIG. 61 is an outboard end view of a further alternative drive ringarrangement.

FIG. 62 is a perspective view of the alternative drive ring arrangementshown in FIG. 61.

FIG. 63 is a partially sectioned view of the drive ring shown in FIG.62.

FIG. 64 is a perspective view of a deformable resilient body comprisinga compression spring.

FIG. 65 is an outboard end view of an alternative disc housingarrangement.

FIG. 66 is a perspective view of the alternative disc housingarrangement shown in FIG. 65.

FIG. 67 is a partially sectioned view of the disc housing shown in FIG.66.

FIG. 68 is an exploded view of the deformable resilient body comprisingnested coil springs that are used in the disc housing of FIG. 65.

FIG. 69 is an end view of a further alternative disc housing.

FIG. 70 is a perspective view of the alternative disc housing shown inFIG. 69.

FIG. 71 is a partially sectioned view of the disc housing shown in FIG.70.

FIG. 72 is a perspective view of the deformable resilient bodies used inthe disc housing of FIG. 69.

FIG. 73 is an exploded view of an inner housing ring and outer housingring of an alternative disc housing.

FIG. 74 is an end view of the alternative disc housing shown in FIG. 73.

FIG. 75 is a perspective view of the alternative disc housing shown inFIG. 74.

FIG. 76 is a partially sectioned view of the disc housing shown in FIG.75.

FIG. 77 is a perspective view of the deformable resilient body used inthe alternative disc housing of FIG. 74.

FIG. 78 is a cross-sectional view of an alternative clutch arrangementwith the disc housing of FIGS. 56-59 attached to a flywheel of a driverwhich is shown in phantom.

FIG. 79 is an end view of an exemplary vibration damping separator disc.

FIG. 80 is a cross-sectional view of the vibration damping separatordisc shown in FIG. 79.

FIG. 81 is a perspective view of the vibration damping separator discshown in FIG. 79.

FIG. 82 is an exploded view of the vibration damping separator discshown in FIG. 79.

FIG. 83 is an axial cross-sectional view of a disc pack of a clutchincluding the vibration damping separator discs shown in FIG. 79.

FIG. 84 is a perspective view of the disc pack shown in FIG. 83.

FIG. 85 is an end view of the disc pack shown in FIG. 83 and thebackplate of the associated clutch.

FIG. 86 is a perspective view of the disc pack and backplate shown inFIG. 85.

FIG. 87 is an axial cross-sectional view of a clutch similar to theclutch shown in FIG. 78 including the vibration damper separator platesof FIGS. 79-82.

FIG. 88 is a plan view of an alternative vibration damping separatorplate.

FIG. 89 is a cross-sectional view of the vibration damping separatorplate shown in FIG. 88.

FIG. 90 is a perspective view of the vibration damping separator plateshown in FIG. 88.

FIG. 91 is exploded view of the vibration damping separator plate shownin FIG. 88.

FIG. 92 is a cross-sectional view of a clutch disc pack including thevibration damping separator plates of FIG. 88.

FIG. 93 is a perspective view of the disc pack shown in FIG. 92.

FIG. 94 is an end view of the disc pack shown in FIG. 92.

FIG. 95 is a perspective view of the disc pack shown in FIG. 92.

FIG. 96 is a cross-sectional view of an exemplary clutch that includesthe vibration damping separator plates similar to FIG. 87 but alsoincluding the vibration damping disc housing similar to FIG. 78.

DETAILED DESCRIPTION

It will be readily understood that features of exemplary embodiments maybe arranged and designed in a wide variety of different configurations.Thus the following detailed description of the exemplary apparatus andmethod embodiments is not intended to limit the scope of the claimsappended hereto, but are merely representative of selected exemplaryembodiments that implement the principles described herein.

The features, structures and/or characteristics described herein may becombined in any suitable manner in one or more embodiments orarrangements. That is, a particular feature, structure or characteristicdescribed in connection with one embodiment may be included in otherembodiments or arrangements.

Referring now to the drawings and particularly to FIG. 1, there is showntherein an exemplary embodiment of a ship or other seagoing vesselgenerally indicated 10. The exemplary embodiment of the ship 10 as shownin this partially transparent view includes a pair of engines 12.Engines 12 drive respective azimuth thrusters 14. Thrusters 14 includepropellers that are driven by the engines 12 to propel the ship 10.

The exemplary arrangement further includes a pair of electric generatorsets 16. The generator sets include electrical generators powered byrespective engines. The generator sets 16 are suitable for producingelectricity used in the operation of the ship.

As shown in more detail in FIG. 2 engines 12 of the exemplaryembodiment, each have attached thereto a mechanical clutch 18. Clutches18 may be one of the types of clutches described herein. Each of theclutches is in operative connection with a drive shaft 20. Drive shaft20 of the exemplary embodiment is a lightweight high strength shaft suchas a carbon fiber shaft. Each shaft 20 is connected by couplings 22 tothe clutch assembly 18 and the azimuth thrusters 14. Each of the azimuththrusters is in connection with a gear box 24. Each gear box is inconnection with a mechanical clutch 26.

In the exemplary arrangement each engine 12 has mounted on an endopposite to clutch 18, a firefighting pump 28. The firefighting pumps 28are used to pump water such as may be used in a fire boat application toshoot water onto a fire. Each of the firefighting pumps 28 is driventhrough a respective clutch 30.

In the exemplary arrangement each of the generator sets 16 includes anengine such as a diesel engine which is connected to an electricalgenerator. The generator is operatively connected to the engine throughclutches 32. It should be understood that in the exemplary embodimenteach of the clutches may be selectively controlled to mechanicallyengage and disengage the driven device which is alternatively referredto herein as a load, from the driver device, which is alternativelyreferred to herein as a driver. In some arrangements the clutches may beactuated by air. In such cases the clutches may be engaged anddisengaged through the application of pneumatic pressure. Such pneumaticpressure may be applied and released through appropriate valves thatchange condition responsive to control circuitry. Alternatively in otherarrangements the clutches may be engaged and disengaged via hydraulicpressure. Hydraulic pressure actuated clutches like those describedhereafter are engaged and disengaged via the application and release ofhydraulic pressure. The hydraulic pressure can be controlled throughappropriate valves and circuitry. The particular type of clutch utilizeddepends on the particular application and the nature of the force andspeed that need to be controlled. It should be understood that theclutches described herein are but examples of the numerous varieties ofclutches that may be used in the applications discussed.

FIG. 3 shows an exemplary embodiment of a clutch 34. Clutch 34 is ahydraulic actuated clutch that may be used to selectively engage adriver such as an engine to a driven device or rotatable load such as agenerator, propeller or a pump. The driven device generally constitutesa load that has an associated load force that must be overcome to berotated by the driver device. The exemplary clutch 34 includes a housing36. Housing 36 includes a mounting flange portion 38. Flange portion 38includes openings through which fasteners may be extended as shown, toattach the housing 36 to a bell housing or other structure associatedwith a driver. The exemplary housing 36 includes a plurality of openings40. Openings 40 extend in the annular and radially extending sides ofthe housing to facilitate cooling of clutch components within theinterior of the housing.

Clutch 34 includes a shaft 42 which has a coupling 44 thereon. Coupling44 is mounted in fixed engagement with the shaft 42. As can beappreciated, FIGS. 3-5 only shows one half of the coupling arrangementwhich would couple the shaft 42 to a drive shaft or other suitabledriven structure.

As best shown in the cross-sectional view in FIG. 5, clutch 34 includesan input coupling 46. Coupling 46 couples to a flywheel of an engine orother member of a driver. In some embodiments the coupling 46 may be avibration damping coupling of the types later discussed herein. Coupling46 is in operative connection with a rotatable clutch disc housing 48.Clutch disc housing 48 is rotatable relative to the shaft 42 on bearingsas shown.

A plurality of spaced clutch discs 50 which may alternatively bereferred to herein as friction discs, are positioned in the clutch dischousing 48. In the exemplary embodiment the clutch discs have outercircumferential toothed edges which are alternatively referred to assplines, at the outer periphery that engage with correspondinglycontoured grooves which are alternatively referred to as splines whichare elongated in the axial direction on the interior annular face of thedisc housing 48. This arrangement enables the clutch discs 50 to move inthe axial direction within the disc housing.

Intermediate of each adjacent pair of clutch discs within the dischousing is a separator disc 52. Each separator disc includes a toothedannular inside contour that engagingly conforms with a splined hubportion 54. Hub portion 54 is attached to the shaft and rotatestherewith. The configuration of the splined hub and the toothedseparator discs enables the separator discs to move in the axialdirection on the splined hub.

In the exemplary embodiment the disc housing 48 includes therein avariable volume piston cavity 56. Cavity 56 is sized to enable axialmovement of an annular piston 58 therein. Cavity 56 is operativelyconnected to a fluid passage 60. Hydraulic pressure applied to the fluidpassage 60 causes cavity volume to increase and the piston to move tothe left as shown in FIG. 5. Movement of the piston to the left causesthe clutch discs and separator discs to be axially compressed and movedrelative to the disc housing and the hub portion. As the separator discsand clutch discs are axially compressed by the piston, the separatordiscs can no longer rotationally move relative to the clutch discs. Thisengages the clutch so that rotation of the coupling 46 causes the shaft42 to rotate in coordination therewith.

As can be appreciated, relieving the hydraulic pressure from the cavity56 causes cavity volume to decrease and the piston to no longer compressthe discs and to retract to the right as shown in FIG. 5. The retractionof the piston is aided through the operation of springs 62. As thepiston moves to the right, the force on the previously axiallycompressed friction discs and separator discs is relieved. This enablesthe friction discs and the separator discs to again rotationally moverelative to one another. In such condition the clutch is disengaged. Ofcourse it should be understood that this structure is exemplary and inother embodiments other approaches may be used.

As represented in FIG. 5, clutch 34 includes a clutch actuation fluidcoupling 64. Clutch actuation fluid coupling 64 includes an opening 66which is fluidly connected to a hydraulic fluid line through a suitablefitting. Opening 66 remains stationary relative to the rotating shaft.The exemplary clutch actuation coupling 64 further includes a pair ofoutlet ports 68. Outlet ports 68 provide a drain to allow hydraulicfluid that is used to lubricate the clutch actuation coupling to drainout of the coupling structure.

The exemplary clutch actuation coupling is shown in more detail in FIGS.6-8. The exemplary clutch actuation coupling includes an annular sleeve70. Annular sleeve 70 overlies and extends in surrounding relation ofthe exterior surface of shaft 42 which is also referred to herein as ashaft outer face. Sleeve 70 is maintained in fluid tight engagement withthe outer face of the shaft by annular resilient seals such as O rings72 as shown. The sleeve 70 is held in relatively fixed rotationalengagement with the shaft 42 through fasteners such as set screws 74.The set screws extend in an annular flange portion 75 of the sleeve.

The fluid openings 66 and 68 extend in an annular body 76. Annular body76 extends in surrounding relation of the sleeve and is able to maintainits stationary rotational position because it is movably supported onthe sleeve through a pair of disposed bearings 78. Flange portion 75includes a radially extending step 77 and one of the bearings ispositioned in adjacent relation with the step 77. Another bearing ispositioned between a step on the sleeve and a locking ring as shown. Afluid passage 80 extends through the body 76. The fluid passage 80extends generally radially between an outer face and an inner face ofthe body. A central block member 82 is in operative engagement with thebody 76 at the annular inner face thereof. Block member 82 includes afluid passage therethrough 84. The inner annular face of block member 82of the exemplary embodiment is slightly radially disposed from the outerannular face 83 of annular sleeve member 70. This slight spacing is usedto enable axial flow of hydraulic fluid for purposes of providingcontrolled lubrication flow as later discussed. However, it should beunderstood that in other embodiments the block member may have an innerannular face in abutting engagement with an outer annular face of thesleeve and the outer annular face of the block member may be radiallydisposed from the inner annular face of the body so as to enable axialliquid flow therebetween.

A pair of seals 86 are axially disposed on each side of block member 82.In the exemplary embodiment seals 86 are comprised of resilient materialand provide a fluid tight seal at each end of the cavity of the body 76in which the block member is positioned. Each of seals 76 in theexemplary embodiment is disposed in adjacent inboard relation to abearing 78. Each of the exemplary seals is in operative attachedengagement with the body. Each seal 86 includes a flexible inwardextending annular lip 87. The annular lips are configured to be incontacting engagement with the relatively moving sleeve outer face 83.However, in other embodiments the seals may be configured to be inrotationally fixed operative engagement with the sleeve and the flexiblelips or other sealing members configured to be in contact with an innerface of the body.

In the exemplary arrangement the passage 80 through the body 76 andpassage 84 through the block member 82 are in fluid communication withan annular recess 88 that extends around the outer diameter of thesleeve member 70. The annular recess 88 is in fluid communication with apassage 90 through the sleeve member 70. Passage 90 is in fluidcommunication with a radially extending branch 92 of the fluid passage60. Also as represented in FIGS. 7-8, resilient annular seals 72 extendannularly in sealing engagement between the inner face of the sleeve andthe outer face of the shaft 72 on each axial side of the passage 90. Asa result fluid leakage from the area of the passage 90 through the spacebetween the sleeve and the shaft is prevented.

In operation, fluid used for actuating the clutch is provided through afitting or similar connector through opening 66. The applied fluidpressure acts through the passage 80 in body 76 and through the passage84 in block member 82 to reach the annular recess 88. The fluid pressureacting in the annular recess of the sleeve acts through the opening 90in the sleeve such that fluid pressure is applied in branch 92 and fluidpassage 60. Sufficient fluid pressure acting through the couplingengaged with opening 66 will move the piston to compress the clutchdiscs and separator discs so as to engage the clutch. Withdrawing thefluid pressure at opening 66 to a suitably low level causes the pistonof the clutch and causes the clutch to retract and separator discs todisengage and become relatively rotationally movable.

A useful feature of the exemplary clutch actuation fluid coupling isthat the inner annular face of the block member 82 is slightly disposedradially away from the outer annular surface of the sleeve member 70.This provides a small annular passage that provides controlled fluidflow in both axial directions from the passage 84 in the area betweenthe block member and the sleeve. This fluid flow operates to cause theliquid hydraulic fluid to flow into contacting relation with the lips ofthe resilient seals 86 that are engaged with the outer face 83 of thesleeve. The fluid moves axially into cavities 89 that are bounded by theradially extending block side walls 91, the seals 86, the inner face ofthe body and sleeve outer face 83. The fluid reaching the resilient sealcontact points serves to lubricate areas of engagement between the seallips and the sleeve. Further the flow of fluid through the cavities 89helps to provide a cooling effect as well as to remove any debris orother material that might otherwise be present within the cavities 89.

The fluid that passes between the block member 82 and the outer diameterof the sleeve 70 is drained from the cavity through outlet passageswhich are alternatively referred to as ports 68. Thus the exemplaryarrangement can provide a generally continuous flow of lubricating andcooling fluid through the clutch actuation coupling so as to providereliable operation and long life.

Further in the exemplary arrangement the coupling structures arefabricated to exact tolerances and have smooth polished finishes so asto provide precise locations and smooth engagement between thecomponents of the clutch actuation coupling. The exemplary arrangementwhich provides for sealed engagement between the sleeve and the shaftavoids the need for the outer face of the shaft to be smooth and highlypolished or perfectly symmetrical as any imperfections are accommodatedby the plurality of annular seals 72 that extend between the inner faceof the sleeve and the outer circumference of the shaft. Rather in theexemplary arrangement the flexible lips 87 contact the smoothed andpolished outer face 83 of the sleeve which can provide reliable sealingand extended seal life. Further the exemplary arrangement includes sealsthat extend annularly on each axial side adjacent to passage 90 throughthe sleeve to the fluid passage 60 within the shaft. The positioning ofthese resilient annular seals prevents leakage of fluid between thesleeve and the shaft so as to provide reliable application of pressureto engage the clutch. Of course it should be understood that while theexemplary clutch actuation fluid coupling 64 has advantages, itsfeatures are exemplary and in other embodiments other or differentstructures or arrangements may be used.

FIGS. 9-13 show an alternative exemplary embodiment that includes aclutch 94. Clutch 94 of this exemplary embodiment is a slipping clutchmeaning that it is designed to operate for extended periods with thedriver and the driven device only partially engaged such that the drivendevice rotates at a speed that is different than the rotational speed ofthe driver. Clutch 94 may have particular applicability in marineapplications such as in circumstances where it may be desirable tooperate the propellers included in thrusters at a rotational speed thatdiffers from the speed at which such propellers would rotate if theclutch were rigidly engaged with the driver. This approach might beuseful, for example, when a marine engine is being operated to driveboth a water pump for firefighting applications and the thrusters of theship. In such circumstances it may be desirable to turn the water pumpdeveloping the water flow for use in fighting the fire at a very highrate of speed while the thrusters are only driven at a relatively lowrate of speed as necessary for the ship to maintain the desired positionrelative to the object on which the water is being sprayed. Of coursethis is only one example of an application for the type of clutch 94.

The exemplary clutch 94 includes a housing 96. A shaft 98 extends fromthe housing and a coupling 100 is attached thereto. In the exemplaryembodiment the clutch housing 96 is connected through a flange portion102 to a gear housing which is alternatively referred to as a gear box104. In the exemplary embodiment the gear box 104 houses suitable gearssuch as a ring gear, planetary gears or other suitable gear sets thatinclude gears that can be engaged with gear driven devices throughopenings at multiple angularly spaced locations on the gear box. Forexample in the exemplary embodiment, the gear box 104 is shownoperatively connected with a pair of gear driven pumps 106, 108. As canbe seen from the figures, the exemplary embodiment of the gear box 104includes five angularly spaced openings and mounting locations foraccessory gear driven devices. For the device mounting locations where adevice is not connected, the opening that can be used to access thegears located in the gear box can be covered by a removable cover plate110. Exemplary embodiments may include features like those described inU.S. Provisional Application Ser. No. 62/248,347 filed Oct. 30, 2015 andapplication Ser. No. 15/334,015 filed Oct. 25, 2016 the disclosures ofeach of which are incorporated herein by reference in their entirety.

In the exemplary embodiment, the gear box is in operative connectionwith a bell housing 112. The bell housing 112 includes a flange 114 orother suitable connecting portion that can be used to engage the bellhousing with an engine or other suitable driver device. The exemplarybell housing houses a rotatable dampening coupling 116. Coupling 116includes vibration reducing resilient materials and other suitablestructures that reduce the propagation of undesirable vibrations andother forces from the engine or other driving members into the gear boxand clutch. The coupling 116 of the exemplary embodiment is adapted tobe engaged with a flywheel or other suitable rotating member of theengine or other driving member. Of course in other embodiments othertypes of couplings which can engage the clutch with driver or drivendevices can be used or alternatively the vibration damping arrangementsthat are later described herein.

The exemplary slipping clutch 94 is shown in cross-section and ingreater detail in FIGS. 12 and 13. In the exemplary arrangement thecoupling 116 which is rotated by the engine and operatively connected toan input shaft 118 that extends in and operatively drives the devices ofthe gear box. The input shaft 118 is operatively connected to agenerally cylindrical disc housing 120. Disc housing 120 is a generallycylindrical housing that houses clutch discs and separator discs of adisc pack which may be similar to those previously discussed. The shaft98 extends in the disc housing 120 and is rotatable relative theretowhen the clutch is disengaged.

As best shown in FIG. 13, a hub portion 122 is attached to shaft 98 androtates therewith. Hub portion 122 includes an axially splined hubportion. The axially extending splined hub portion 122 includes axiallyelongated hub splines that are configured to rotationally engage andenable relative axial movement of a plurality of separator discs 124thereon. The exemplary separator discs include an inner splined diameterthat is configured to engage the splined portion of the hub. The dischousing includes an axially splined internal annular surface 126.Splined surface 126 included angularly spaced inward directed axiallyelongated splines configured to rotationally engage the outer toothedcontours of the radially outward directed splines on outer splinedcircumference of a plurality of clutch discs 128. In the exemplaryembodiment the clutch discs and separator discs are arranged inalternating relation with the clutch discs engaged through their outersplined diameter toothed contours with the annular inward splinedsurface of the disc housing, and the separator discs engaged throughtheir inner splined diameter toothed contours with the splined hubportion.

In the exemplary arrangement the disc housing includes an annular cavity130. Cavity 130 houses a movable annular piston 132 which is movabletherein. An annular pressure plate 134 is positioned between the piston132 and the disc pack comprising the clutch and separator discs. Abacking plate 136 extends on the opposite side of the disc pack from thepressure plate 134.

As in the previously discussed embodiment, a clutch actuation fluidcoupling 138 overlies the shaft 98 and is usable to supply fluidpressure to an actuator fluid passage 140. The clutch actuation fluidcoupling 138 may include features similar to those discussed inconnection with coupling 64.

Supplying pressure to the opening 142 is operative to cause fluidpressure to be applied behind the piston 132 in cavity 130. This causesthe volume of the cavity to increase and the piston 132 to move axiallyto the left as shown in FIGS. 12 and 13. Movement of the pistoncorrespondingly axially moves the pressure plate 134 and selectivelyaxially moves and compresses the separator and clutch discs axially inthe disc pack so as to engage the clutch. When fluid pressure isrelieved from the fluid passage 140, springs 144 act to retract thepiston 132 decreasing the volume of the cavity. This enables the discsin the disc pack to axially move apart and to rotationally move relativeto one another resulting in disengagement of the clutch.

The exemplary embodiment of slipping clutch 94 operates to maintain theclutch discs and separator discs in a fluid bathed environment. Liquidtransmission fluid is passed radially outward between the discs of thedisc pack in order to provide cooling and to carry away any debris thatmay be generated during clutch operation. Further in this exemplaryembodiment because the clutch may be operated in a slipping mode for anextended period of time without damage, the liquid material extending onand between the discs operates to transmit rotational torque throughfluid shear forces in circumstances where the clutch and separator discsare not contactingly engaged and/or are not fully compressively engaged.

In the exemplary arrangement the transmission fluid which passes throughthe disc pack is supplied by suitable fittings to a clutch fluidcoupling. In some arrangements this may be a fluid coupling similar tothe clutch actuation fluid coupling that was previously described inconnection with supplying fluid for actuating the piston.

The transmission fluid that is alternatively referred to herein ascooling oil or cooling fluid, flows through a transmission passage 146that extends in the shaft 98. The fluid passage is in connection with amanifold chamber 148 in the hub portion 122. The manifold chamber isconnected to a plurality of fluid openings 150. The fluid openings 150extend into the spaces between the grooves of the spline in the hubportion. This enables the transmission fluid to flow radially outwardbetween the separator discs and clutch discs. In exemplary embodimentscentrifugal force aids in moving the liquid in the outward direction.

In the exemplary arrangement the transmission fluid that flows betweenthe discs moves radially outward away from the hub portion to theannular periphery of the disc housing 120 and splined annular surface126. The transmission fluid that is moved radially outward passesthrough fluid outlet openings in the hub portion and drains into thegenerally fluid tight housing 96 of clutch 94. In the exemplaryarrangement the oil is drained from the interior of the housing and iscollected in a tank. From the tank the fluid can be returned by a pumpto the transmission fluid passage of the clutch. As can be appreciatedin some exemplary arrangements, the fluid circuit for the transmissionfluid may include a heat exchanger or other suitable device to maintainthe temperature of the fluid and the clutch within a desired operatingrange. In addition in some arrangements the fluid circuits may includesuitable filters or other devices for removing debris or otherimpurities that may be entrained in the transmission fluid. Of coursethese approaches are exemplary and in other embodiments, otherarrangements may be used.

FIG. 32 shows an alternative clutch arrangement generally indicated 300.Clutch arrangement 300 includes a housing 302. Housing 302 includes manyfeatures like those previously described. Clutch 300 includes a flangeportion 304 which is configured for connecting the clutch housing to adriving member such as a diesel engine or other device. Clutch 300further includes an output shaft 306.

As shown in FIG. 33, housing 302 houses a clutch 308. The clutch mayhave features similar to clutches previously described. Clutch 308includes a disc housing 310 which houses clutch discs and separatordiscs in a disc pack like that previously discussed. The disc housing310 is in operative rotatable connection with a driving member such asthe engine crankshaft through an anti-vibration flex plate or similarcoupling structure, or includes the vibration damping features laterdiscussed herein.

Shaft 306 includes therein a shaft coolant fluid (CF) passage 312. ShaftCF passage 312 is configured to deliver coolant in the form oftransmission fluid to a manifold 314 at the inside diameter of theclutch and separator discs. Shaft CF passage 312 delivers transmissionfluid that is enabled to pass radially outward through the clutch andseparator discs in a manner like that previously discussed to providecooling for the clutch discs during operation. Housing 302 includes aninterior sump area 316 which captures the transmission fluid which ispassed through the clutch discs and separator discs so that it can becooled in a fluid circuit and again passed through the separator discs.

Shaft 306 further includes a shaft actuation fluid (AF) fluid passage318. Shaft AF passage 318 is in fluid communication with an annularpiston chamber in the housing 310. AF fluid pressure applied to passage318 is operative to move a clutch piston 320 to the left as shown inFIG. 33. Movement of the piston 320 in response to AF pressure causesthe clutch and separator discs to be compressed and causes the shaft 306to rotate with the driving member which is connected to the dischousing. Releasing the AF pressure from the passage 318 enables piston320 to be retracted to the right and allows the clutch to be disengagedso that the disc housing may rotate without causing rotation of theshaft.

In the exemplary clutch 300, a fluid coupling 320 shown in cross sectionin FIG. 34 is utilized to deliver CF and AF to the clutch. The housing320 includes a central bore 322 through which shaft 306 extends in theoperative position of the coupling. The bore extends about a centralaxis 324 which is a common central axis with shaft 306.

The exemplary coupling 320 includes an annular body 326. Body 326includes an annular body outer face 328 and an annular body inner face330. A body CF passage 332 extends generally radially through the body326. The body CF passage is in fluid connection with a body CF outeropening 334 which extends in the outer body face 328. The body CFpassage 332 further connects with a body CF inner opening 336 whichextends in the body inner face 330.

An annular sleeve 338 extends in surrounding relation of the shaft 306.The exemplary sleeve 338 includes an annular sleeve inner face 340 andan annular sleeve outer face 342.

A sleeve CF passage 344 extends between a sleeve CF outer opening 346 onthe sleeve outer face and a sleeve CF inner opening 348 on the sleeveinner face 340. Sleeve 338 includes an annular recess 350 that extendsabout the sleeve in diametric alignment with the sleeve fluid passage.As can be appreciated, the annular recess enables CF to be in fluidcommunication with the sleeve CF inner opening regardless of the angularposition of the sleeve relative to the body 326.

As shown in FIG. 33, the shaft CF passage 312 includes a radiallyextending portion 352 which terminates in a shaft CF inlet opening 354in the annular shaft outer face 356. The shaft CF inlet opening 354 isaligned with the sleeve CF inner opening so that CF may flow through thesleeve and into the shaft CF passage 312.

A pair of resilient annular seals 358, 360 are positioned in recesses inthe sleeve inner face on opposed axial sides of the sleeve CF inneropening 348 and the shaft CF inlet opening 354. Each of the resilientseals extends in abutting fluid tight relation between the shaft outerface 356 and sleeve inner face 340. The pair of resilient seals 358 and360 operate to assure that fluid does not escape by moving in an axialdirection between the sleeve inner face 340 and the shaft outer face356, thus assuring that fluid is transmitted effectively from the sleeveCF passage 344 into the shaft CF passage 312.

The exemplary coupling 320 includes fasteners 362 which operate toengage the sleeve 338 and the shaft 306. The fasteners help to assurethat the sleeve 338 rotates in relatively fixed engaged relation withthe shaft 306.

A pair of axially disposed bearings 364 and 366 are operativelypositioned between the sleeve 338 and the body 326. The bearings 364 and366 enable the relative rotational movement of the sleeve 338 and thebody 326. As can be appreciated in the exemplary coupling arrangement,the body 326 remains stationary as the sleeve 338 and the shaft 306rotate therein.

A CF block 368 is positioned intermediate of the body inner face 330 andthe sleeve outer face 342. In the exemplary embodiment, block 368 has anannular block outer face 370 that is in abutting engaged relation withthe body inner face 330. Block 368 also has a block inner face 372 thatis adjacent and slightly radially disposed from the sleeve outer face342. The block inner face 372 and the sleeve outer face 342 bound a CFgap 374. Gap 374 has a radial distance that is sized to provideclearance to enable controlled axial CF flow therethrough in a mannerthat is later discussed.

Block 368 further includes a block passage 376 that extendstherethrough. Block passage 376 extends between the block outer face 370and the block inner face 372. Block passage 376 is aligned and in fluidcommunication with the body CF inner opening 336. Passage 376 is also influid communication with the gap 374 and the annular recess 350 which isin turn in fluid communication with the sleeve CF passage 344 and theshaft CF passage 312.

Block 368 further includes a radially extending annular block outer sidewall 378. Block outer side wall 378 is axially disposed inwardly frombearing 366. Side wall 378 and bearing 366 define a CF fluid manifoldspace 380. CF passes from the CF gap 374, into space 380. To lubricateand cool the bearing 366, CF passes from space 380 and through thebearing.

Block 368 is bounded axially inward by an annular radially extending CFblock inner side wall 382. Block inner side wall 382 bounds one axialside of an equalization chamber 384. The equalization chamber 384 isconnected to equalization ports 386 and 388, the purpose of which islater explained.

The exemplary coupling 320 further includes a body AF passage 390. BodyAF passage 390 extends generally radially through the body 326 and isaxially disposed from the body CF passage 332. The body AF passageextends from a body AF outer opening 392 on the annular body outersurface 328 to a body AF inner opening 394 which extends in the bodyinner face 330.

The sleeve includes a sleeve AF passage 396. The sleeve AF passageextends between a sleeve AF inner opening 398 in the sleeve inner face340 and a sleeve AF outer opening 400. The sleeve outer face 342includes an annular recess 402 that is fluidly connected with the sleeveAF outer opening 400. The recess 402 enables the body AF passage 390 tobe in fluid communication with the sleeve AF passage 396 regardless ofthe relative angular position of the sleeve with respect to the body.

The sleeve AF inner opening is generally aligned with a radiallyextending portion 404 of the shaft AF passage 318 as shown in FIG. 33.The shaft AF passage 318 includes a shaft AF inlet opening 406 that isin radially aligned relation with sleeve AF passage 396.

A pair of annular resilient seals 408 and 410 extend in annular recessesin the sleeve inner surface 340. Similar to seals 358 and 360, seals 408and 410 extend in fluid tight abutting relation between the annularshaft outer face 356 and the sleeve inner face 340. Seals 408 and 410are disposed on opposed axial sides of the sleeve AF inner opening 398and the shaft AF inlet opening 406. The pair of seals 408 and 410generally prevent the flow in an axial direction of AF in the spacewhich extends between the shaft outer face 356 and the sleeve inner face340. This enables the fluid to effectively flow from the sleeve into theshaft AF passage so as to move the piston 320 without loss of fluid.Further in the exemplary embodiment additional annular resilient sealsindicated 412 extend between the sleeve inner face 340 and the shaftouter face 356. The seals 412 are positioned axially away from the areasbounded by seal pairs 408, 410 and 358, 360. Although two additionalseals 312 are shown, other embodiments may include no additional sealsor other numbers of such additional seals.

The exemplary coupling 320 further includes an AF block 414. Block 414extends intermediate of the body inner face 330 and the sleeve outerface 342. Block 414 includes a block passage 416. Block passage 416extends between a block annular inner face 418 and a block outer face420.

The exemplary block outer face 420 is in abutting relation and inengagement with the body inner face 330. As a result, block 416 isengaged with body 326 and remains stationary while the shaft 306 and thesleeve 338 rotate relative thereto. The block inner face 418 is disposeda first radial distance from the sleeve outer face 342 so as to providean annular clearance AF gap 422 therebetween. Similar to the CF gap 374,the AF gap 422 enables axial flow of the AF in the gap between the blockinner face 418 and the sleeve outer face 342.

Block 414 includes a generally radially extending AF block inner sidewall 424. Side wall 424 is axially disposed from side wall 382 of CFblock 368. Side wall 424 and side wall 382 axially bound theequalization chamber 384.

CF block 414 further includes an outer side wall 426. Outer side wall426 is disposed axially inward of bearing 364. Side wall 426 and thebearing define an AF fluid manifold space 428. AF fluid manifold space428 is an annular space through which AF that has passed axially outwardthrough the gap 422 may flow and then subsequently pass through thebearing 364 for coolant and lubrication purposes.

As shown in greater detail in FIGS. 35 and 36, the controlled radialclearance spaces provided by CF gap 374 and AF gap 422, enable fluidwhich can be either CF or AF from the adjacent port to move axially inthe gaps between the adjacent block inner surface and the sleeve outersurface. As represented in FIG. 36, the body CF passage 332 enables theCF to flow radially inward therethrough and inwardly through the CFblock passage 376 in the CF block 368. The fluid in block fluid passage376 largely flows into the sleeve CF passage 344. However, thecontrolled clearance of the annular radial gap 374 enables some of theCF to flow axially outward from CF block passage 376 through the annularCF manifold space 380. From the CF manifold space 380, the fluid flowsaxially outward through bearing 366 as represented by arrows O.

The fluid also flows axially inward from the block passage 376 throughthe CF gap 374 and the annular equalization chamber 384. The fluidreaching the equalization chamber 384 passes outward through one of theequalization ports 388. This is represented by the arrow I.

As can be appreciated, the exemplary coupling structures associated withthe actuation fluid operate in a manner similar to that described inconnection with FIG. 36 for the coolant fluid. AF fluid pressure appliedthrough the body AF passage 390 and the AF block passage 416 generallypass through the shaft AF passage to move the piston 320. However, someof the AF moves axially outward through the AF gap 422, through the AFfluid manifold space 420 and through the bearing 364. AF fluid alsomoves through the AF gap 422 axially inward to the equalization chamber384. The AF fluid then passes outwardly through one of the equalizationports 388.

Of course it should be appreciated that in this exemplary arrangementthe actuation fluid AF and the coolant fluid CF each comprise the sametransmission fluid which is used in separate fluid streams for actuationand cooling purposes. In the exemplary arrangement, the fluid iscollected in the sump area 316 of the housing 302. A stream of the fluidis then elevated in pressure by one or more pumps and controlled throughvalves for purposes of piston actuation in a manner like that previouslydescribed. Another fluid stream is pumped and directed for cooling orotherwise directed for use as the CF for purposes of cooling the clutchand lubricating the bearings of the coupling and/or other components ofthe clutch 300. Of course it should be understood that this arrangementis exemplary and in other embodiments, other arrangements may be used.

For example in some arrangements, different actuation fluids and coolantfluids may be utilized and the streams thereof kept separate. This maybe accomplished by using additional seals or other structures within thecoupling arrangement and the clutch housing. Further, other arrangementsmay include additional structures to provide controlled flow patterns soas to direct the actuation fluid and the coolant fluid along particularpaths within the fluid coupling. For example in some arrangements theblock inner face, sleeve outer face or both may include helicalprojections and/or recesses which may operate to direct fluid in theannular gap in a desired axial direction. This may be done, for example,if it is desired to increase the rate of fluid flow in the gap forcoolant or lubrication purposes. This approach may also be taken incases where fluids are axially directed in the gap so as to helpmaintain separation between different types of coolant fluids andactuation fluids. Further in some exemplary embodiments the annular gapmay be pressurized via fluid from a port such as for example port 488 toachieve fluid movement in the gap in a desired axial direction. Forexample, pressure may be applied at an axial inward port so as to forceaxial movement of fluid axially outward through the bearing.

It should further be understood that the size of the radial clearancegap may be different for actuation fluid and coolant fluid. For examplein some arrangements the coolant fluid may flow at a higher rate but ata lower pressure than the actuation fluid, which may experiencerelatively little flow compared to the coolant fluid. In sucharrangements, the size of the radial gap may differ so as to enablesufficient flow of coolant fluid to reach the bearing 366. The radialgap for the actuation fluid may be smaller because of the elevatedpressure used for purposes of piston actuation, which enables adequatelubrication and cooling fluid flow through bearing 364 of the exemplaryembodiment even though the AF gap may be smaller than the CF gap. Ofcourse these configurations are exemplary and in other embodiments,other approaches may be used.

Further, in the exemplary coupling 320 two fluid passages are provided.However, it should be understood that the principles described hereinmay be applied to couplings having only one fluid passage. Likewise theprinciples may be applied to coupling structures that handle more thantwo fluid flow streams for purposes of delivering fluids from astationary outer body to a relatively rotating internal sleeve and shaftstructure.

Of course it should be appreciated that in the exemplary arrangement,the sleeve outer surface is generally a much more uniform and smoothsurface than the outer surface of the shaft. This enables providing fora uniform and precisely sized radial clearance gap between the innerface of the block and the outer face of the sleeve. Providing thisprecise clearance enables achieving a more uniform and predictable flowfor cooling and lubrication through the coupling. Also it should beappreciated that different embodiments may be configured to havedifferent configuration blocks so as to control the annular gap to moreprecisely meet the requirements of a given application and theparticular fluid type and pressures to be handled by the coupling. Theprinciples described herein can be used for such purposes to achievesatisfactory operation in numerous different operating environments.

FIGS. 14-19 show various forms of clutch discs which includearrangements of liquid holding grooves therein. In these exemplaryembodiments the clutch discs are comprised of a metal disc with highfriction material on each opposed axial side. As previously discussed,because in operation each clutch disc has an adjacent separator disc oneach side, each surface including the high friction material is adjacentto and when the clutch is fully engaged, in compressed engagementagainst separator disc within the clutch disc pack.

FIGS. 14-19 show exemplary arrangements of grooves that may be includedin friction material of exemplary clutch discs. As can be appreciated,the grooves in such discs provides fluid holding flow passages for thetransmission fluid that passes radially outward through the disc pack.Further the grooves also provide passageways for the transmission fluidand enables flow even when the clutch discs and separator discs arebeing held in abutting engagement. In the exemplary embodiment, thisfacilitates the cooling flow of the transmission fluid through the discpack. Further as can be appreciated in some exemplary arrangements, theorientation of the grooves in the friction material may facilitate theflow of transmission fluid radially outward through the grooves inresponse to centrifugal force created by the rotation of the disc pack.Exemplary grooves include radially extending grooves, circumferentiallyextending grooves and combinations thereof.

In the exemplary arrangement, the clutch may operate as a slippingclutch such that the speed of the engine or other driver device can bemaintained at a much higher rate of rotational speed than the outputshaft of the clutch and the driven device in operatively fixedrotational engagement therewith. In such arrangements, the fluid heldentrained within the grooves may operate to transmit torque between theclutch discs and the separator discs based on the rotational movement ofthe fluid within the passages. This transmission of torque can beachieved based on the amount, flow and viscosity of the transmissionfluid as well as the finish of the adjacent separator discs. Thus as canbe appreciated, the rotational movement and torque of the engine may beat least partially transmitted through the disc pack via the fluid shearforce of the rotating liquid. Further in some exemplary arrangements,the amount of the force transmitted may be selectively varied bymovement of the piston to selectively vary the proximity of the clutchdiscs and separator discs in slip positions when the discs are not indirect contact. Thus for example having the fluid of the passages of theclutch discs in proximity to the separator discs will effectivelytransfer more rotational movement torque via fluid coupling effects inslip positions when the discs are in very close, non-contacting axialproximity than when the discs are disposed further axially apart.

As can be appreciated, these properties of enabling movement and forcetransmission when the clutch and separator discs are not in contactingengagement, can be useful in a number of different operating conditions.For example, in the exemplary arrangement shown in FIG. 2 where theengine drives not only the thrusters but also a firefighting pump, therewill be circumstances where the full water flow through the firefightingpump is desirable. This may mean that the engine is operated at arelatively high rotational speed. However, the thrusters may only needto move at a relatively much slower rotational speed than would beachieved if the clutch were fully engaged. In these circumstances,selectively varying the axial distance between the discs included in thedisc pack in a non-contact slip condition enables the exemplary clutch94 to operate the thrusters at a selected much slower rotational speedthan the rotational speed of the engine.

In addition, exemplary arrangements of the clutch may also provide thecapability to avoid the shock and vibration that would otherwise ariseupon full rigid contacting engagement of the clutch discs of aconventional clutch. For example in this exemplary arrangementrotational movement and force is being transmitted between the clutchdiscs and the separator discs as the discs move in closer proximity inresponse to axial movement of the piston and eventually engage incompressed contacting engagement. This enables the output shaft of theclutch to begin rotating at a relatively slow speed in slip positions ofthe piston and to then have the speed increase as desired to the levelof the driver member as the discs increasingly contactingly andcompressively engage. This “soft engagement” capability avoidsunnecessary wear on clutch components as well as the devices that aredriven through the clutch. Of course it should be understood that theseapproaches are exemplary and in other embodiments, other approaches maybe used.

In the exemplary embodiment of slipping clutch 94, the adjacentseparator discs 124 and clutch discs 128 are biased away from oneanother by springs. In one exemplary arrangement the springs compriseserrated Belleville springs such as spring 152 shown in FIG. 22. Theexemplary Belleville spring 152 includes a toothed serrated contour onits inner diameter 154 that conforms to the splined contour of hubportion 122. This contour enables the spring to move in the axialdirection relative to the hub portion during actuation of the clutch andcompression of the spring, while preventing rotational movement relativeto the hub portion. This is shown in greater detail in FIGS. 20 and 21.

The exemplary serrated Belleville spring configuration 152 furtherincludes an outer diameter having a serrated contour 156. The serratedcontour includes projections 158 and recesses 160. The projections 158provide the effect of fins for purposes of facilitating heat transfer.The recesses 160 provide for allowing fluid flow radially outward acrossthe springs. The exemplary springs further include in cross section aconsistent outwardly angled or canted contour in one direction.

FIG. 23 shows a cross-sectional view of the arrangement of springs 152,separator discs 124 and clutch discs 128 in a disc pack of an exemplaryembodiment. As shown in the exemplary arrangement, the springs 152 arearranged in sequentially opposite canted directions in the disc pack.This approach is used to provide more balanced separating forces appliedby the springs to the adjacent separator discs. Thus as can beappreciated from FIG. 23, the exemplary arrangement operates to maintainclutch discs and separator discs spaced apart in the disengagedcondition of the clutch. However, with movement of the piston 132 toengage the clutch, the force of the piston overcomes the force of thesprings 152 to cause the clutch discs and separator discs to move closertogether. As this happens, the transmitted rotational torque initiallydue to shear forces of the liquid causes increased fluid couplingeffects and rotational and torque transmission while the discs “slip”relative to one another. Bringing the discs into closer proximitythrough selective movement of the piston in slip positions increases theamount of torque that is transmitted solely by fluid effects. Thetransmission of rotational movement is increased as the clutch discs andseparator discs begin to contact and press against one another. Thetorque of the engine is fully transmitted when the piston has axiallycompressed the discs in engaged relation to the maximum extent and theclutch and separator discs are rotating in unison. Of course it shouldbe understood that these approaches are exemplary and in otherembodiments other arrangements may be used. Further it should beunderstood that while in the exemplary embodiment the driver device isin fixed operative rotational connection with the disc housing and thedriven device is in fixed operative rotational connection with theshaft, in other clutch arrangements the relationships may be reversed.

FIG. 24 shows schematically an exemplary control system that is used tocontrol the operation of a slipping clutch such as clutch 94. Aspreviously discussed, the slipping clutch may be particularly useful inapplications where the driver device advantageously operates at a higherspeed and at least one driven device operates at a substantially lowerspeed. One exemplary application of this type is in the ship examplepreviously discussed where the engine advantageously operates a waterpump for pumping firefighting water at a high speed while the thrustersare operated by the engine at a much lower speed as a result of slippingof the clutch. Of course this is only one of many such applicationswhere approaches of this type are advantageously used.

In the ship used for firefighting example, the ship will commonly beequipped with a GPS positioning system such as the one schematicallyindicated 162 in FIG. 24. Such a positioning system may communicate withGPS satellites to determine the position of the ship. Further in theexemplary arrangement the positioning system may operate to resolve thecommands necessary to control the ship's thrusters in order for the shipto hold a particular position despite the effects of wind, waves, firenozzle thrust and other things that may be acting to try to move theship. As can be appreciated, the exemplary positioning system includescontrol circuitry including processors, data stores with computerexecutable instructions and other appropriate electronic components. Thesystem determines the desired position to be held and resolves thenecessary messages to be issued to the different electronicallycontrolled components of the ship so as to accomplish holding the shipin the desired position. Of course it should be understood that this maybe but one function of such a positioning system, and many otherfunctions may be capable of being carried out depending on the nature ofthe positioning system and its programming.

As represented in FIG. 24, the positioning system is operativelyconnected to clutch control circuitry 164. The exemplary controlcircuitry which is alternatively referred to herein as a circuit, mayinclude one or more of a microprocessor, CPU, FPGA, ASIC or other typeof circuit that is capable of executing instructions. The data store mayinclude one or more of a volatile or nonvolatile memory device or mediumincluding RAM, CD, DVD, flash memory, hard drive, solid state drive,magnetic memory, optical storage memory or other medium which dataand/or machine executable instructions can be stored. The clutch controlcircuitry of the exemplary embodiment includes one or moremicroprocessors 166. The clutch control circuitry also includes one ormore data stores 168. Data stores 168 may be any one of the differenttypes of media suitable for storing thereon computer executableinstructions and computer readable data. Such data stores in exemplaryembodiments may include, for example, hard drives, solid state memories,programmable read-only memories, random access memory or other similarcomputer readable media.

In the exemplary embodiment the clutch control circuitry is connectedthrough one or more interfaces 170 with sensing devices schematicallyrepresented 172, 174 and 176. In the exemplary arrangement sensor 172 isoperative to sense the input speed of the slipping clutch. This may bedone by determining the rotational speed of the engine. Alternativelythis may be accomplished by sensing the rotational speed of one or morecomponents in the gear box or other mechanism that rotates at a speedthat corresponds to the speed of the engine.

Sensing device 174 senses the output speed of a component thatcorresponds to output speed of the shaft of the clutch. The output speedsensor may include a sensor that senses one or more elements on theoutput shaft. Alternatively it can sense elements moving on or withcouplings, drive shafts or other suitable components whose speedcorresponds to the speed of the clutch shaft.

Sensor 176 comprises one or more temperature sensors. This temperaturesensor may be operative to sense the temperature of one or moredifferent components or items associated with the clutch. For example,the temperature sensor may sense the external or internal housingtemperature. Alternatively or in addition, sensors may sense thetemperature of the transmission fluid/cooling oil in or after leavingthe housing. Other sensors may sense the temperature of transmissionfluid/cooling oil that is entering the clutch housing. Other sensors maysense the temperature of the fluid used to activate the clutch.Alternatively other sensors may sense the temperature at the surface ofclutch discs or other components. Numerous different types of sensorsmay be used for such purposes.

It should be understood that the sensing devices discussed are exemplaryand in other arrangements different, additional or other types ofsensors may be included to sense parameters that are desirably sensedfor purposes of controlling the slipping clutch.

The exemplary clutch control circuitry is further in operativeconnection with an interface 178. Interface 178 is in operativeconnection with a pressure control valve 180. The pressure control valve180 is a hydraulic control valve. In the exemplary embodiment valve 180operates to control the fluid pressure that is applied in the actuatorfluid passage to move the piston 132 so as to relatively axiallyposition the clutch and separator discs. Valve 180 is operative tocontrol hydraulic fluid pressure supplied by a pump 182 that is appliedto the actuator fluid passage 140 which controls movement of the pistonwithin the clutch 94. Pump 182 is supplied with hydraulic fluid from atank 184. Tank 184 receives hydraulic fluid from the drain ports of thefluid coupling which is in connection with the shaft of the clutch. Ofcourse it should be understood that this fluid circuit is exemplary andin other embodiments other approaches may be used.

The clutch control circuitry 164 is also in operative connection with aninterface 186. Interface 186 is in operative connection with a coolingflow control valve 188. Valve 188 controls the flow rate of transmissionfluid through the transmission fluid passage and the disc pack of theclutch. Flow control valve 188 is supplied with transmission fluid by apump 190. Pump 190 is supplied with fluid from a holding tank 192.Holding tank 192 is supplied with liquid that is drained from the clutchhousing. Further as shown in this exemplary fluid circuit, a heatexchanger 194 may be included in the fluid circuit to cool and maintainthe temperature of the transmission fluid/cooling oil in a temperaturerange that provides for efficient operation of the clutch and whichminimizes wear on the clutch components.

In the exemplary arrangement the positioning system is operated to holdthe position of the ship and communicates with the clutch controlcircuitry to operate the thrusters at the speed necessary to hold theship at the desired position. Of course it should be understood thatwhile the system shown in FIG. 24 operates to control the speed of theoutput shaft of the clutch and thus the speed of the associatedthrusters, the positioning system of an exemplary embodiment would alsobe in communication with appropriate circuitry and control systems thatcontrol the direction in which the thrusters are pointed.

The control circuitry 164 responds to the electrical commands ofpositioning system 162 to speed up or slow down the output shaft of theclutch so as to cause the thrusters to operate at the speed necessary tohold the desired position. In doing this, the clutch control circuitryuses the information from the sensors to monitor input speed, the outputspeed and the temperature and other parameters associated with theclutch. The control circuitry then operates to send signals whichcontrol the pressure control valve as desired to change the output speedof the clutch. In addition in the exemplary arrangement the clutchcontrol also operates to control the rate of transmission fluid/coolingoil through the clutch so as to maintain the temperature of the clutchat the desired level for purposes of allowing the clutch to slip whilestill providing the desired degree of torque transmission.

Further in some exemplary arrangements the control circuitry may operateto cease cooling the transmission fluid and/or control or stop the flowof transmission fluid under appropriate conditions by controlling one ormore transmission fluid handling components. For example, incircumstances in which slipping or partial engagement of the clutchcauses high heat generation, the control circuitry may operate inaccordance with its programming to send control signals throughappropriate interfaces to cause the heat exchanger fan or other coolingdevice to operate at maximum cooling capability. In addition the controlcircuitry may cause the pump and cooling flow control valve to operateat high flow. If the clutch condition is changed so it is fully engaged(or alternatively fully disengaged) the amount of heat generated by theclutch is reduced. In response to sensing the lower temperature theexemplary control circuitry may operate in accordance with itsprogramming to reduce the speed or stop the fan or other cooling deviceassociated with the heat exchanger. Alternatively or in addition, thecontrol circuitry may cause the pump to operate at a slower speed and/orchange the condition of the flow control valve to provide less flow oftransmission fluid through the clutch. Upon further cooling of theclutch the exemplary control circuitry may operate to shut off the heatexchanger cooling device, the pump and/or the valve. Taking such actionswhen cooling is not needed can be done to save energy and to reduceoperating time and wear of the fluid handling components. Of coursethese approaches are exemplary and other control systems may controlclutch temperature via different methods of operation.

Of course as can be appreciated, if the positioning system senses thatthe ship is moving away from the desired position despite the currentspeed of rotation of the associated thruster, the positioning systemwill cause the clutch control circuitry to increase the speed of theoutput shaft of the clutch. Likewise if the positioning systemdetermines that the thrusters are providing more thrust than isnecessary to hold the ship in the desired position, the positioningsystem will send signals which cause the control circuitry to providegreater slipping of the clutch and thus lower the speed of rotation tothe associated azimuth thruster. Of course it should be understood thatthe control system is exemplary and the description is simplified, andin other arrangements, other approaches may be used.

An advantage of the exemplary slipping clutch and ship drive controlsystem of the exemplary embodiment is that it can avoid the need foradditional equipment that would otherwise be needed to accomplish thesame function. The exemplary system can also accomplish the slipping andcontrol functions more effectively than other approaches. Specificallysome arrangements may include an intermediate transmission devicebetween the engine and the thruster. Such an intermediate device oftenadds considerably more weight to the drive system for the ship, whichcan be undesirable. In addition, such intermediate transmission devicesconsume energy which can lower efficiencies. A further issue that issometimes encountered is that the use of such an intermediate device canresult in additional drive shafts and driven shafts as well as universaljoints to connect the intermediate device to the driving and drivenmembers. Such additional shafts and universal joints also can lowerefficiencies. These disadvantages can be reduced through the use of theexemplary clutches and systems that have been described.

FIG. 25 shows a schematic transparent view of a ship 196. Ship 196includes a diesel electric hybrid drive system generally indicated 198.The exemplary hybrid drive system is shown in greater detail in FIG. 26.The hybrid drive system includes azimuth thrusters 200 which may besimilar to those previously described. Like the previously describedthrusters, the angle of the thrusters is selectively controllable. Eachof the thrusters are driven through a respective gear box 202. The gearbox 202 is driven through a clutch 204.

Each thruster gear box is operatively connected to a motor generator206. Each motor generator is connected through a shaft to an engine 208such as a diesel engine. The engine 208 is operatively connected to themotor generator through a clutch 210. In this exemplary arrangement,clutch 210 may be similar to clutch 34 previously described. Clutch 210in the exemplary embodiment generally is not a slipping clutch. However,it should be understood that in other arrangements slipping clutches orother types of clutches may be used.

As further represented in FIG. 26, each of the diesel engines 208 isoperative to drive a firefighting pump 212. Each of the firefightingpumps are operatively connected to the engine through a respectiveclutch 214.

The exemplary arrangement further includes generator sets 216. Eachgenerator set 216 includes a diesel engine and an electric generator.Each electric generator is in operative connection with the enginethrough a clutch 218. The exemplary system further includes batterypacks 220 as well as control circuitry 222. Of course it should beunderstood that these components of the hybrid drive system 198 areexemplary and in other arrangements, different, other or additionalcomponents may also be included. Some exemplary arrangements may utilizefeatures like those described in U.S. patent application Ser. No.15/333,992 filed Oct. 25, 2016 the disclosure of which is incorporatedherein by reference in its entirety.

In operation, the hybrid drive system may operate in a number ofdifferent modes. For example in one mode of operation, a diesel engine208 may drive an azimuth thruster by engaging clutches 210 and 204. Insuch circumstances the intermediate motor generator 208 may befreewheeling. Alternatively in other circumstances the motor generatormay be loaded so as to generate electricity from the rotation providedby the diesel engine 208.

In an alternative mode of operation, a thruster may be driven throughoperation of a motor generator 206. In these circumstances clutch 210may be disengaged while clutch 204 on the azimuth thruster may beengaged. In this condition the motor generator which is supplied withpower either from the generator sets 216 or from the batteries 220 mayoperate to power the thruster.

In still another arrangement which is similar, the clutch 214 whichdrives the firefighting pump 212 could be engaged while clutch 210 isdisengaged and the thruster is driven by the motor generator 206. Inthis condition, the firefighting pump capacity is controlled by thespeed of the engine 208 while the speed of the azimuth thruster iscontrolled by the speed of the motor generator. This can provide fortotally independent and different speeds for the firefighting pump andthe azimuth thruster without the need for a slipping clutch.

In still another alternative arrangement of the system shown, the clutch204 on the azimuth thruster may be disengaged while clutch 210 whichconnects the engine 208 and the motor generator 206 is engaged. In thiscondition the engine 208 can be used to drive the motor generator so asto produce electricity.

As can be appreciated, this exemplary hybrid drive system arrangementprovides many different optional operating configurations which can beused to best serve the particular functions that are needed for a givenship condition or other operating environment. Of course as can beappreciated the approaches described are exemplary and in otherembodiments, other approaches may be used.

FIGS. 27-29 show yet another exemplary embodiment of a clutch 224.Clutch 224 is configured to be actuated through the application ofcompressed air rather than liquid hydraulic fluid, however theprinciples may be applied to clutches actuated in either manner. Furtherthe exemplary clutch 224 is configured to provide enhanced air coolingas well as other features that enable the clutch to be advantageouslyused in many different types of power transmission applications.

Clutch 224 includes a housing 226. Housing 226 is a generallycylindrical housing. The clutch includes a disc housing which isalternatively referred to as a drive ring 228. Drive ring 228 includes aplurality of openings 230 configured for extending fastenerstherethrough. The drive ring may be connected in fixed operativeengagement with a driver member such as a rotating member connected toan engine or to a driven member such as a pump, generator or otherstructure so as to selectively transmit rotational energy thereto.

The drive ring of the clutch housing further includes a splined innerannular surface 232. Splined surface 232 has a toothed configuration soas to matingly engage with the toothed annular outer circumferenceconfiguration that includes clutch disc splines of friction clutch discs234. The splined annular surface 232 includes a plurality of angularlyspaced radially inward facing outer splines that are axially elongatedand enable the clutch discs to axially move in engagement therewith.Clutch 224 further includes a hub portion 236. Hub portion 236 includesa bore 238 that in an exemplary embodiment is configured to receive ashaft therethrough. The shaft, hub and housing are rotatable about anaxis 284.

Hub 236 includes four discrete splined angularly spaced arcuate segments240. The arcuate segments extend between air containing openings 242.The arcuate segments each have axially splined toothed surfaces 244. Thetoothed surfaces have radially outwardly directed inner splines that areconfigured to engage the inside annular toothed surface of separatordiscs 246. Each of the clutch discs 234 have an inner surface that isdisposed radially outward from the inner splines, and each of theseparator discs 246 have an outer surface that is disposed radiallyinward from the outer splines. As can be appreciated, the frictionclutch discs 234 and the separator discs 246 comprise a disc pack andare enabled to relatively move axially within the housing. The clutchdiscs move with their toothed circumferential outside surfaces inconforming engagement with outer splines on splined surface 232 whilethe separator discs 246 move with their circumferential toothed surfacesat the inner surfaces in engagement with the inner splines 244 includedin arcuate segments 240.

The housing 226 includes an annular piston cavity 248. An annular piston250 is configured to be movable axially in the piston cavity 248.Resilient seals 252, 254 provide fluid tight movable engagement betweenthe opposed surfaces of the piston and the wall bounding the pistoncavity 248 including inner and outer cavity walls 302, 304. In theexemplary arrangement the seals 252 and 254 are X-shape seals whichprovide a multi-point sealing engagement arrangement to minimize airloss around the seals and to help assure that the piston supplies thedesired level of force when axially compressing the clutch discs andseparator discs which make up the disc pack. Further in the exemplaryarrangement a wiper seal 256 operatively extends between the outerannular cavity wall of the piston cavity and the piston at the radiallyoutward side of the piston. Wiper seal 256 of the exemplary arrangementserves to reduce the infiltration of debris and other material into thearea between the piston cavity and the piston. The wiper seal 256 alsohelps to avoid debris reaching the inboard seal 254, which debris orother material may wear or otherwise render seal 254 less effective.

The exemplary piston cavity at its enclosed end is in operativeconnection with a fluid passage 258. Fluid passage 258 may beselectively operatively connected with a source of compressed air, whichwhen pressure is applied, operates to urge the piston 250 to move to theleft as shown in FIGS. 28 and 29.

In the exemplary arrangement, the plurality of angularly spacedanti-rotation guide pins 260 extend into the piston cavity and intorecesses 262 in piston 250. Pins 260 are held in place by lock nuts 264or similar structures. The interior cylindrical portions of pins 260 aresized so as to be movable within recesses which are also referred to asguide slots 262 that extend in the piston. As a result, the piston 250is movable in an axial direction relative to guide pins 260 but isprevented from rotationally relatively moving with respect to the hubportion by the pins 260. This helps to assure transmission of rotationalmovement. Of course it should be understood that this approach isexemplary and in other arrangements, other approaches may be used.

Guide pins 266 extend axially in engagement with the hub portion in thearea of each of the air containing openings 242. Each of the guide pinsincludes an engageable top portion 268. Top portion 268 includes a hexhead or similar suitably configured portion so as to enable the guidepins to be rotated via a tool into threaded or similar fixed engagementwith the hub portion. Compression springs 270 extend in surroundingrelation of each guide pin 266. Springs 270 operate to bias spacers 272to the right as shown in FIGS. 28 and 29. Each of spacers 272 include aforward face 274. The forward face biasingly engages the pressure plate276 and biases the pressure plate and the piston in an axial directiontoward the piston cavity. Pressure plate 276 is an annular pressureplate that extends axially intermediate of the piston 250 and a first ofthe clutch discs 234 in closest proximity to the piston as shown.Projections 278 extend axially outward from each of the spacers and areaxially movably engaged in a respective one of recesses 279 which extendin the pressure plate, so as to maintain the rotational positionedalignment of the pressure plate therewith.

In the exemplary embodiment each of the spacers 272 further includes incross section radially extending fingers 280,282. Fingers 280 and 282are configured to engage respective separator discs 246 in the areas ofthe openings. Fingers 280 and 282 bias the separator discs axially in adirection toward the piston and piston cavity. Because the separatordiscs are biased by the spacers 272 in the four locations of theopenings, the separator discs and the pressure plate 276 are generallyuniformly axially biased by the springs toward the piston 250.

In operation of an exemplary embodiment, a rotational driver or drivendevice is operatively engaged with the drive ring 228. For purposes ofthis example, the operation of the clutch will be described with adriver such as a rotating member attached to an engine in operativeconnection with the drive ring. The drive ring is rotated by the enginewhich causes the area of the clutch 224 in operative connection with thedrive ring and the spline surface 232 to rotate in fixed directoperative connection therewith.

Rotation of the spline surface 232 causes the friction clutch discs 234to rotate therewith. The shaft or other driven member that extends inthe bore 238 of the hub portion in this example is a driven member infixed direct operative connection with the driven device. The driveshaft extends along an axis 284 through the hub portion. When airpressure is not applied to the piston cavity, the piston 250 isretracted in the axial direction within the cavity due to the biasingforce applied by springs 270 which act on the piston through the spacers272 which bias the pressure plate 276. Spacers 272 through the fingers280 and 282 also bias the separator discs 246 toward the pressure plateand the piston. The biasing of the separator discs in the axialdirection also causes the clutch discs 234 to be moved in the axialdirection.

With compressed air pressure not acting on the piston, forces actingbetween the clutch discs 234 and the separator discs 236 enable thediscs to rotationally move relative to one another. As a result therotation of the drive ring 228 does not cause the hub portion 236 torotate. As a result, the shaft or other driven member that extendsthrough the bore 238 of the hub portion is not caused to rotate.

Applying air pressure to the fluid passage 258 causes the piston 250 tomove axially to the left as shown in FIGS. 28 and 29. Movement of thepiston overcomes the relatively smaller biasing force of the springs 270and causes the pressure plate 276 to move in the axial direction to theleft as shown. Movement of the pressure plate causes the clutch discsand separator discs to be in axially compressed engagement. Thecompression of the discs in the disc pack causes the discs to be firmlyengaged. As a result the driving force applied to the drive ring 228 iseffectively transferred through the disc pack to the hub portion 236which rotates in engagement therewith. This causes the shaft or othermember which extends in the bore to also rotate in coordinated relationwith the drive ring.

Removing the fluid pressure from the passage 238 leading to the pistoncavity releases the force previously applied by the piston 250 tocompress the discs. The pressure plate 276 and the friction discs andseparator discs 234 and 246 are again moved by the force of the springsso that the discs are no longer in compressed engagement. The force ofsprings 270 acts through the spacers 272. As a result the clutch discsand separator discs again become relatively rotationally movable and theclutch is disengaged.

The exemplary configuration of the clutch 224 includes a plurality ofangularly spaced threaded bores 286. Bores 286 which serve as actuatoropenings extend from outside of the housing and into the piston cavity248. Threaded bores 286 are generally fluidly closed by plugs 288 thatare at least partially threaded therein. In the exemplary embodiment ifconditions arise where it is not possible to supply air pressure toactuate the clutch, the plugs 288 may be removed from the bores 286.Threaded bolts or other pins or similar members may be threaded into thebores 286 so as to engage the back of the annular piston 250. Theannular piston 250 may be moved by such members being threaded in thebores so as to axially move the piston in a manner similar to thatcaused by air pressure so as to engage the clutch. This enables thedriving and driven members to be solidly engaged even in situationswhere the clutch could not be engaged in the normal manner. Thisapproach is highly useful in emergency situations where the clutch canbe engaged on a manual basis. Further the solid piston construction ofthe exemplary arrangement enables the use of this emergency techniquefor purposes of actuating the clutch.

In some exemplary arrangements to provide additional cooling of theclutch discs, the annular area 290 of the drive ring and the splinesurface 232 may include one or more slotted openings 291. The slottedair containing openings may extend in the circumferential directioncircumferentially across the splines of surface 232. Alternatively or inaddition the air containing openings may extend in a direction parallelto the axis. In some arrangements such opening may span more than oneclutch disc. The openings may provide passages for air flow through theclutch to facilitate the cooling of the discs. In addition such openingsmay also provide a means for debris and other material that is generatedby the action of the clutch to escape from the interior of the housing.This may facilitate the reliable operation of the clutch under hightemperature and other extreme operating conditions. Further in someexemplary arrangements provisions may be made for air containingpassages or other suitable grooving arrangements through the discs orother surfaces to help facilitate cooling in the areas of the frictionand separator discs. In other exemplary arrangements fins may beutilized to establish greater air movement through the air containingspaces. Of course the approaches used can be varied depending on theoperating environment in which the clutch is utilized.

In some exemplary embodiments of the clutch 224, clutch discs of thetype shown in FIGS. 30 and 31 may be used. Clutch discs 292 are of aunitary molded composite construction which is comprised of twodifferent materials. A core portion 294 is comprised of a fiberreinforced polymer material. Core 294 includes the central disc portionas well as the teeth of the toothed outer annular portion engage anannular splined surface such as spline surface 232 of clutch 224. Inexemplary embodiments the core 294 may be comprised of carbon or glassfiber reinforced polymers which provide for a rigid, strong andlightweight torque transmitting structure for the disc.

The exemplary clutch disc 292 further includes a pair of annular opposedmolded friction surfaces 296. Friction surfaces 296 are comprised ofmolded high friction material which includes suitable carbon fibers orother types of materials that provide high friction engagement betweenthe friction surfaces and the adjacent separator discs. In the exemplaryembodiment the clutch discs 292 may be manufactured via pressurizedmolding operations that cause the constituents which make up the coreand friction surfaces be bound together in a strong unitary discstructure that is able to withstand high temperatures, pressures and therotational forces which are encountered in a clutch disc environment.Further a useful aspect of the exemplary clutch disc structure is thatit may be dimensioned so as to be a direct replacement for other typesof clutch discs that are made of separately assembled support andfriction elements. Of course it should be understood that these featuresare exemplary and in other embodiments other approaches may be used.

FIG. 37 shows an exemplary vibration damping coupling 430. Coupling 430may be used in systems in a manner similar to coupling 116 previouslydiscussed. Vibration damping coupling 430 includes a first portion 432.First portion 432 is an outer annular portion of the coupling and isconfigured to be attached in direct operative connection with a drivermember such as the flywheel of an engine. Coupling 116 further includesa second portion 434. Portion 434 comprises an inner portion and isconfigured for direct operative connection with the driven device whichcomprises a rotatable load such as a propeller, a grinder, a woodchipper, mixer, pump, winch or other load, through the clutch. In theexemplary arrangement portion 432 is rotationally movable relative toportion 434. Outer portion 432 includes openings 436 that are used withfasteners to connect the outer portion to the flywheel or other drivermember. Inner portion 434 includes openings 438 that are used withfasteners for connecting the inner portion to the clutch and drivenmember. The inner portion 434 also includes a hub 440. The hub 440 issuitable for engaging components of the clutch or other driven member.

The exemplary coupling 430 further includes a plurality of resilientbodies 442. In the exemplary arrangement the resilient bodies arecomprised of a plurality of cylindrical rollers. The rollers extend incylindrical openings between the outer portion 432 and the inner portion434, and operatively engage such portions so that they rotate together.In the exemplary arrangement the resilient bodies 442 provide fordeflection and vibration absorption so as to reduce the transmission ofknock and vibration forces from the driver member such as an engine, tothe driven member through the clutch. Of course it should be understoodthat this coupling configuration is but one of many different types ofvibration damping coupling constructions that may be used.

In the exemplary arrangement coupling status sensors 446, 448 arepositioned adjacent to coupling 430. The coupling status sensors areoperative to detect at least one condition corresponding to thedeformation of the resilient bodies 442. In the exemplary arrangementthe coupling status sensors are operative to detect the relativerotational positions of the inner portion 434 and the outer portion 432.In the exemplary arrangement the sensors may include Hall Effect sensorsthat are operative to detect bodies with magnetic properties that movein adjacent relation to the sensor. In the exemplary arrangement anindicator 450 is in attached connection with outer portion 432. Anindicator 452 is in attached connection with inner portion 434. Each ofthe respective sensors 446, 448 are operative to detect when therespective indicator is positioned adjacent thereto and to producesignals responsive thereto. This enables the coupling status sensors todetect the extent to which the resilient bodies 442 are currentlycompressed. This is accomplished in the exemplary arrangement bydetermining the amount that the signal from the sensor 448 is laggingbehind the signal from the sensor 446.

As can be appreciated, because the outer portion 432 is attached to thedriver device, and the inner portion 434 is attached through the clutchto the load, the applied loading on the inner portion 434 will causecompression of the bodies 442 that operatively connect the inner andouter portions of the coupling. The greater the force of the load themore the bodies 442 are compressed. The more the bodies are compressedthe greater the lag between when the indicator 450 on the outer portionof the coupling is sensed by the sensor 446 and when the indicator 452on the inner portion 434 is sensed by the sensor 448. In exemplaryembodiments this ability to analyze the signals from the coupling statussensors enables determining the deformation of the resilient bodies aswell as the magnitude of the load that is currently being applied by thedriven device.

It should further be understood that in an exemplary arrangement thecoupling status sensors may also be used for purposes of determining thelevel of wear of the coupling as well as coupling malfunctions. Forexample if a condition is detected where the outer portion 432 isrotating but the inner portion 434 is not, then this is an indicationthat the coupling has broken. Further, excessive relative movement ofthe inner and outer portions may be indicative of a wear condition andan impending failure of the coupling. Numerous different conditions maybe detected through analysis of the signals which are received from thecoupling status sensors. Of course this approach to sensing thedeformation of the resilient bodies in the coupling is exemplary and inother embodiments other approaches may be used.

FIG. 39 is a schematic representation of a control system used forcontrolling operation of the clutch 454. This clutch control system issomewhat similar to the system described in connection with the slippingclutch 94 previously described in connection with FIG. 24. In thisexemplary arrangement clutch 454 is not operated as a slipping typeclutch. However, features of the exemplary arrangement described inconnection with FIG. 39 may be used with slipping clutches and in othersystems. Further while the exemplary system associated with clutch 454is for a liquid actuated and liquid cooled clutch, features that theexemplary system may also be utilized in connection with air cooledclutches and pneumatically actuated clutches.

In the exemplary system a clutch control circuit 456 controls theoperation of the clutch 454. The exemplary clutch control circuitincludes structures like those described in circuit 164, including atleast one processor schematically indicated 458. The processor includesa timer 460 such as a clock function of the processor. The processor isin operative connection with at least one data store 462. The data store462 includes circuit executable instructions, operating data and otherdata used in connection with the operation of the system. As used hereinreferences to a circuit or circuitry will encompass a single circuit aswell as multiple circuits that are in operative connection.

A user interface 464 is in operative connection with the control circuit456. User interface 464 of the exemplary embodiment includes inputdevices and output devices. In the exemplary embodiment the inputdevices may include pushbuttons schematically indicated 466. Thepushbuttons may include a start button, a jog button, a speed controlbutton, a stop button or other suitable button, dial, lever, switch orother types of devices from which inputs may be received from anoperator. The exemplary user interface further includes output devicessuch as a display 468 and a wireless transmitter 470. In an exemplaryarrangement the display 468 may be operative to provide the user withinstructions, operating conditions, status indications, faultindications or other information regarding operation of the system. Inother exemplary arrangements other types of output devices such asaudible annunciators, light indicators or other types of output devicesmay be provided. In some exemplary arrangements certain devices mayprovide both input and output device functions such as a touchscreen. Ofcourse it should be understood that the user interface 464 is exemplaryand in other embodiments other types of user interface devices may beused.

In the exemplary system the clutch 454 is controlled responsive tohydraulic pressure. The hydraulic pressure is supplied by a pump 472.The pump 472 provides hydraulic fluid at an elevated pressure that issupplied from a tank 474. The high-pressure hydraulic fluid supplied bythe pump is selectively delivered at a controlled pressure through apressure control valve 476. The valve 476 may selectively applyhydraulic pressure to and release pressure from a piston cavity of theclutch 454 to respectively engage and disengage the clutch. This may bedone in a manner like that previously discussed in connection with theother hydraulic actuated clutches that have been described herein. In anexemplary arrangement valve 476 may comprise a pulse width modulatedvalve which can selectively supply and release pressure to the pistoncavity at different pressure levels in response to signals sent from thecontrol circuit 456 through a suitable interface 478.

In the exemplary arrangement the control circuit 456 may operate thevalve 476 to supply pressure to the piston cavity at a selected pressurelevel to cause the discs in the disc pack to be axially compressedsufficient to engage the clutch. When the clutch is to be disengaged thecontrol circuitry 456 operates the valve to disengage the clutch byreleasing pressure from the piston cavity, which causes the hydraulicfluid to be returned from the valve to the tank 474. The release of thepressure by the valve to a suitable level enables the separator discsand clutch discs in the disc pack to be relatively rotationally movableso that the clutch is disengaged. In exemplary embodiments the controlcircuitry 456 is enabled to vary the pressure applied through the valve476 so as to change the clutch engagement force under certaincircumstances as later discussed. Of course it should be appreciatedthat this approach is exemplary and other embodiments other approachesmay be used.

Similar to the system described in connection with FIG. 24, the clutch454 is a liquid cooled clutch which is cooled by transmission fluid thatis supplied from a tank 480. Although as schematically shown the tank480 for the cooling transmission fluid is a different tank from tank 474that is used for the actuation fluid, in other arrangements the coolingand actuation fluid may both be supplied from a common tank.

In the exemplary system shown a pump 482 is used to supply the coolingfluid to the clutch 454. The flow of cooling fluid is controlled by thecontrol circuit 456 through a flow control valve 484. The flow controlvalve 484 is controlled by the control circuit 456 through a suitableelectronic interface 486. In the exemplary arrangement the cooling fluidmay be passed through the clutch in a manner like that previouslydiscussed in which the cooling fluid carries heat and debris away fromthe discs in the disc pack and other components within the clutch. Inthe exemplary arrangement the cooling fluid which is passed through theclutch is cooled through operation of a heat exchanger 488 before beingreturned to the tank 480. In the exemplary arrangement the controlcircuit 456 may control the operation of the valve 484 as well as theheat exchanger 488 so as to maintain the clutch 454 within a suitableoperating temperature range. Of course it should be understood that thisapproach is exemplary and in other embodiments other approaches may beused.

The exemplary control circuit 456 receives data and other inputs forpurposes of controlling the clutch from a plurality of sensors and otherdevices. For example in the exemplary embodiment shown, the controlcircuit receives an input speed signal from at least one sensor 490.Sensor 490 provides an input speed signal which is indicative of thespeed of the driver device such as the engine to which the clutch isconnected. In some embodiments the input speed sensor 490 may beintegrated in the control circuitry associated with the engine andoutput from an electronic control module associated therewith. In otherarrangements the input speed may be obtained from other sensors such asa sensor in operative connection with the flywheel of the engine. Inother arrangements the input speed may be obtained from a sensor such asthe coupling status sensor 446 previously discussed. Of course theseapproaches are exemplary and other embodiments other sensingarrangements may be used.

Another sensor 492 used in exemplary embodiment serves as an outputspeed sensor. The output speed sensor provides an output speed signalwhich is indicative of the speed of the driven device. The output speedsensor may be in operative connection with the output shaft from theclutch or components of the device which applies the load which isrotationally driven by the driver device. For example in situationswhere the driven device comprises a rotating device such as a pump, awinch, a mixer, a drilling rig, a feed screw, a propeller, a vehicletransmission or other rotational machinery, the output speed sensor 492may be associated with an input shaft to such a device or otherrotational component in connection therewith so that the rotationalspeed thereof is detected. Of course it should be understood that thisarrangement is exemplary and other embodiments other approaches forproviding an output speed signal to the clutch control circuit may beused.

In the exemplary arrangement at least one sensor 494 is used fordetecting a temperature associated with the clutch. In some exemplaryarrangements at least one sensor 494 may be utilized to detect at leastone external or internal temperature of one or more clutch components.This may include for example an external temperature of a portion of thedrive ring, the clutch hub, an input or output shaft, or other clutch orclutch connected component. In other exemplary embodiments sensor 494may be operative to detect a fluid temperature associated with a clutchfluid. This may include in some exemplary arrangements the temperatureof the fluid that is used for purposes of actuating the clutch. In otherexemplary arrangements this may include a temperature associated withthe cooling fluid that is used for purposes of cooling the clutch (insituations where separate fluids are used for the actuation and coolingfunctions).

In an exemplary arrangement the one or more sensors 494 associated withdetecting temperature conditions provide signals to the control circuit456 that are utilized in determining the operational condition andstatus of the clutch. This may include detecting conditions thatcorrespond to potentially damaging conditions or other circumstancesthat may require the control circuit to take actions in accordance withits circuit executable instructions in ways like those later discussedherein.

In the exemplary embodiment at least one sensor 496 is an operativeconnection with the pump 472 for purposes of determining the level ofavailable fluid pressure that can be supplied to the clutch through thevalve 476. In exemplary embodiments sensor 496 may comprise a pressuretransducer that is in operative connection with the pump and/or valveand is operable to determine the fluid pressure available at the valve.In other exemplary arrangements pressure transducers may be positionedto detect fluid pressure that is currently supplied by the valve to theclutch. Further in other exemplary arrangements sensors such as pressuretransducers are positioned in connection with oil filters or other fluidcircuit components for purposes of detecting conditions that maycorrespond to the operating conditions thereof.

In exemplary embodiments at least one coupling status sensor 498 may beoperatively connected to control circuit 456. The at least one couplingstatus sensor may include sensors such as the sensors 446, 448previously discussed in connection with the vibration damping coupling430. Alternatively or in addition other types of sensors may be utilizedin connection with exemplary couplings for purposes of determining thestatus thereof.

In an exemplary arrangement the control circuit 456 is an operativeconnection with at least one load sensor 500. Load sensor 500 of theexemplary embodiment is operative to provide at least one load signalthat is usable to determine the magnitude of the load that is beingapplied by the driven device on the engine and consequently on theclutch 454. In some exemplary arrangements the load signal may beprovided from an electronic control module associated with the driverdevice such as the engine that is in operative connection with theclutch. Some electronic control systems associated with diesel or otherengine types are operative to monitor the applied loading level of thedriving device to manage the components associated with the operation ofthe engine. However in other exemplary arrangements load signals may bedetermined by other sensors that are in operative connection with thedriven device or other devices that are in operative connection with thedriven device. This may include for example in some exemplaryarrangements the coupling status sensors which may be used to determinethe applied load based on the deformation of the resilient bodies in thecoupling that varies with the magnitude of the applied load. Numerousdifferent approaches to obtaining one or load signals that are used bythe control circuitry may be utilized in various embodiments.

In the exemplary arrangement the sensors and other devices communicatewith the control circuit 456 through electronic interfaces schematicallyindicated 502. Some types of sensors may be capable of communicatingthrough a common interface, while other types of sensors and devices maycommunicate through dedicated interfaces. The type of interface utilizedwill depend on the particular sensor or other device that communicateswith the control circuitry in the particular system. Further, it shouldbe understood that while a few examples of sensors and devices have beendescribed in connection with the clutch control system represented inFIG. 39, in other exemplary embodiments numerous different andadditional types of sensors and devices may be utilized depending on theparticular nature of the system in which the clutch is operated.

In some exemplary embodiments the clutch control circuit 456 isoperative to communicate information remotely to other systems. In anexemplary arrangement as represented in FIG. 39, the transmitter 470 isoperative to communicate in a wireless network such as a cellular orWi-Fi network schematically indicated 504. Network 504 may include or bein operative connection with additional networks in which remotecomputers 506 are connected. Such other networks may include local areanetworks or wide area networks such as the Internet. In some exemplaryarrangements the control circuit 456 may be operative to cause theoperating conditions and other information concerning the operation ofthe clutch to be communicated to one or more remote computers 506. Suchconditions may include information about the operating temperatures,applied loads, system status information, malfunctions and otherinformation that is useful for purposes of determining if the clutch andassociated system components are operating properly or may be in need ofrepair or replacement.

Such information may be useful in determining the maintenance and repaircycles for the clutch and associated equipment. Further in exemplaryarrangements such captured and stored data may be useful for purposes ofdetermining if the clutch and associated components have been subject toabuse or extreme operating conditions. The detection of such abuse orextreme conditions may be a basis for assessing additional charges orimposing other requirements in certain circumstances, such as where theequipment that is being utilized is not owned by the operator or is usedon a rental or loaned basis. In other exemplary arrangements theoperating information communicated from the control circuit 456 to thecomputers 506 may be useful for purposes of determining that componentsare operating in ways that suggest they are reaching the end of theiruseful life. This may include for example the coupling status sensorsindicating that the coupling is starting to break down, that the pump isno longer supplying adequate pressure for purposes of actuating thevalve, that the clutch is experiencing excessive slip levels and otherconditions that may be recognized through programmed instructions asindicative of current or developing problems. In some exemplaryarrangements this operating data may be stored in the data storeassociated with the control circuit, rather than sent to a remotecomputer, or in other arrangements the data may be stored in bothplaces. The course these approaches are exemplary and other embodimentsother approaches may be used.

FIGS. 40-46 schematically represent an exemplary logic flow carried outin connection with the operation of clutch 454 through operation of thecontrol circuit 456. It should be understood that this logic flow hasbeen simplified for purposes of explaining the operation of certainfunctions of an exemplary embodiment in a clear and concise manner. Thecontrol logic associated with systems may often include other oradditional features and operations that are not discussed herein.

In an exemplary embodiment the operation of the system will be describedin connection with a driver device such as an engine which is operativeto drive a driven device such as a mixer through the clutch 454. Shouldbe understood that this is merely an example of one of numerousdifferent situations in which the control logic described herein may beutilized.

The control logic will be described beginning at initiation step 508 inwhich the clutch is currently not engaged. In this condition in theexemplary arrangement the driver device which is an engine may berunning, but because the clutch is not engaged it is not expected thatthe driven device would be rotating. From this initiation step thecontrol circuit 456 is operative to receive an engage clutch signal in astep 510. The engage clutch signal in an exemplary arrangement isreceived from the user interface 464 responsive to a manual input from auser corresponding to a pushbutton instruction to engage the clutch. Ofcourse it should be understood that this is exemplary and otherarrangements the engage clutch signal may be received from other typesof manual or electronic devices.

In the exemplary arrangement the control circuit next operates in a step512 to determine the input speed of the driver device. This is done byreceipt of the input speed signal from the sensor 490. In the exemplaryarrangement the at least one data store includes data corresponding to alower input speed limit engagement value. This corresponds to a speed atwhich the engine is required to be operating for satisfactory clutchengagement. In a step 514 the control circuit is operative to determineif the input speed of the driver device is currently above the lowerinput speed limit engagement value. If the input speed is not at thislevel the control circuitry operates to give an indication of thecondition in a step 516. This may be done through an output from thedisplay of user interface 464. In response to this condition the controlcircuitry is operative to cause the logic flow to return to the pointwhere the control circuitry waits for another input, such as anotherinstruction to engage the clutch after the speed of the engine has beenincreased.

If in step 514 the input speed signal of the driver device is determinedto be above the stored lower input speed limit engagement value, thecontrol circuitry causes the logic flow to proceed to a step 518. In theexemplary arrangement the at least one data store includes datacorresponding to an upper input speed limit engagement value. This valuecorresponds to an input speed that is above that which should be presentduring clutch engagement. In step 518 the control logic determines ifthe current input speed signal corresponds to a speed that is above theupper input speed limit engagement value. If the speed is too high thelogic indicates the condition in a step 520 and the logic does notproceed toward engaging the clutch.

If the input speed of the driver device is determined by the controlcircuit to be below the upper input speed limit engagement value in step518, the logic flow proceeds to a step 522. In step 522 the controlcircuit is operative to determine if the output speed signal whichcorresponds to the rotational speed of the driven device is above theinput speed. This condition may happen in connection with some devicesthat may be freewheeling or otherwise driven by other forces external tothe device. Adverse consequences may result to the system if the outputspeed is higher than the input speed when the clutch is engaged. If theoutput speed is determined to be above the input speed at step 522 thecondition is reported at a step 524 and the logic does not proceedtoward clutch engagement.

In an exemplary embodiment the data store associated with controlcircuit includes at least one clutch temperature limit value. Thisclutch temperature limit value corresponds to a temperature at which theclutch should not be engaged so as to avoid damage thereto. In anexemplary arrangement the at least one clutch temperature limit value inthe data store corresponds to temperatures associated with the oil orother fluid that is associated with the actuation of the clutch. In theexemplary arrangement the clutch temperature limit values include adisengagement limit value which when reached during clutch operation,causes the control circuit to operate to cause the clutch to be in adisengaged condition. The exemplary data store further includes are-engagement temperature limit value, which corresponds to atemperature below which the clutch actuation fluid must be before thecontrol circuit will cause the clutch to change from the disengagedcondition to the engaged condition. It should be understood thatalthough in the exemplary embodiment these temperatures are associatedwith the actuation fluid (hydraulic oil) associated with actuating theclutch, in other embodiments the temperature values may be associatedwith temperatures or other items, fluids or structures such as thosepreviously discussed.

In step 526 of the exemplary logic flow the control circuit is operativeto determine the temperature of the clutch actuation fluid based on thesignal from sensor 494. In step 528 the control circuit is operative todetermine if the detected temperature is below the re-engagement limitvalue data that is stored in the data store 462. If the actuating fluidtemperature is not below the re-engagement limit valve, the controlcircuit indicates the condition at a step 530 and does not proceedfurther towards clutch engagement. However if the temperature isdetermined to be below the re-engagement limit value, then the logicproceeds.

In step 532 the control circuit operates to check whether a lockoutstatus has been set due to any conditions that have previously occurredin connection with the system. As later discussed in detail, a number ofdifferent conditions may result in the control circuit setting a lockoutstatus that prevents system operation for a set period of time or untilsome remedial action is taken. In step 534 the control circuitdetermines if a lockout status has been set. If so the condition isindicated in a step 536 and the logic does not proceed toward clutchengagement. However if no lockup status is found, then the logicproceeds to step 538. In step 538 the control circuit causes operationof the valve 476 to apply pressure to the piston cavity so as to engagethe clutch. The control circuit is operative to apply pressure tocompress the disc pack of the clutch at a set level based on theprogramming associated with the control circuit that is usuallysufficient to provide proper engagement of the clutch.

In the exemplary arrangement the data store 462 associated with thecontrol circuit includes data corresponding to a synchronization levelvalue and engagement time value. These values are associated with theprogramming of the control circuit for purposes of assuring that clutchengagement is not attempted under conditions that may damage the clutchor the driving or driven devices. The control circuit also includesexecutable instructions associated with the clutch engagement functionto reduce the risk of such damage or other problems.

As represented in the exemplary control logic by step 540, after thecontrol circuit has operated to apply pressure to the clutch the controlcircuitry is operative to monitor the input speed signal and the outputspeed signals from sensors 490 and 492. At a step 542 the controlcircuit is operative to determine if the input speed signal increaseswith the clutch engagement. If the input speed increases with clutchengagement that may be indicative of a problem. In response to detectingthis condition in step 542 the control circuit is operative to operatethe valve to release the pressure from the piston cavity and disengagethe clutch as indicated in a step 544. The control circuit provides anindication of the condition at a step 546 and returns to the pre-clutchactuation condition.

If a speed increase is not detected in the step 542 the control logicproceeds to a step 548. In step 548 the control circuit operates tocompare the input speed signal and the output speed signal during afixed time window after the valve applies pressure to begin to engagethe clutch. The control circuit is operative to determine if the inputspeed and the output speed have synchronized to at least a level thatcorresponds to the stored synchronization level value within a timewindow as determined by timer 460 that corresponds to the engagementtime. In the exemplary arrangement the synchronization level value is90% within a time window of three seconds after the control circuitryoperates to apply pressure to engage the clutch. Of course, these valuesare exemplary and in other embodiments different synchronization levelvalues and time values may be used.

If the speed as indicated by the output speed signal has not reached atleast 90% of the speed reflected by the input speed signal within theengagement time value of three seconds after start of clutch engagement,this represents a problem in that the driven device is not beingeffectively placed in operation through engagement of the clutch. Such acondition may represent an overload or stall condition with the drivendevice which may cause damage to the clutch. If the synchronizationlevel value is not achieved within a time corresponding to theengagement time value in step 548, the control circuit operates todisengage the clutch and indicate the condition as represented in steps544 and 546 respectively. Alternatively, if the output speed has reachedat least the synchronization level value within the time correspondingto the stored engagement time value, the control circuit operates toprovide an indication that the clutch has properly engaged in a step550. The control circuit maintains this condition until an event occurswhich requires changing the status of the system.

Examples of conditions which are monitored during clutch engagement willnow be discussed in connection with the exemplary control logic. Ofcourse it should be understood that these are merely examples and inother embodiments different, additional or lesser numbers of conditionsmay be monitored by one or more control circuits for purposes ofdetermining a need to change the current system status.

In an exemplary arrangement the control circuit is operative to monitorfor the presence of a status signal from the driver device that it is ina run status. In some exemplary embodiments this may be a signal that isgenerated through the electronic control system of the engine that isdriving the clutch. The monitoring of the signal is represented by astep 552. The control circuit monitors for the presence of this signalas represented in a step 554. If the signal is not present it isindicative of a system problem and the control circuit operates toindicate the condition at a step 556. The exemplary system than furtheroperates as represented in FIG. 46 operate the valve to release thepressure from the piston cavity on the disc pack and disengage theclutch as represented in a step 558. The control circuit then operatesto shut down the system as represented by step 560. The shutdown of thesystem may take different forms and include different steps depending onthe nature of the condition and the system. For example in somearrangements the shutdown may represent an entire shutdown of thedriving device as well as disengagement of the clutch. In otherexemplary embodiments different steps may be taken such as to apply abraking system to the driven device or take other measures asappropriate when a system malfunction occurs. The steps that are takenmay vary depending on the nature of the particular system in which theclutch is used.

If the run signal is determined to be present in step 554, the controlcircuit then operates to monitor the engine speed signal. This isindicated at a step 562. In some exemplary embodiments the electroniccontrol system of the engine or other output device such as atachometer, provides an output to indicate that the engine is rotatingat a particular speed. In some exemplary arrangements this maycorrespond to the input speed signal provided by the sensor 490. Asrepresented in the step 564 the control circuit determines if the speedsignal is present. If the speed signal has been lost, the control logicoperates to indicate the condition at a step 566 and proceeds todisengage the clutch and conduct an appropriate shutdown as previouslyexplained. Also in some exemplary arrangements the circuit may comparethe input speed to an overspeed limit value that is stored in the datastore. If the input speed is determined to be above the overspeed limit,the clutch is disengaged and an appropriate shutdown is conducted.

If the engine speed signal is determined to be present in the step 564,the logic proceeds in a step 568 to determine if a signal is presentfrom the pressure transducer which monitors the pressure available fromthe pump 472 that can be applied through the valve 476 to engage theclutch. In an exemplary arrangement this corresponds to a signal fromsensor 496. In a step 570 the circuit operates to determine if thepressure transducer signal is present. If the signal is not present thisindicates a malfunction and an indication thereof is given at a step 572and the clutch is disengaged as previously discussed.

The exemplary control circuit further operates to determine if thepressure output by the pump 472 is maintained at an adequate pressure.In the exemplary arrangement the data store 462 associated with thecontrol circuit 456 includes data corresponding to a lower pressurelimit value and a pressure time value. These values correspond to aperiod of time during which the pressure may be below the lower pressurelimit value without adverse impact to the system. The exemplary systemoperates to require that the pressure be below the minimum value for aperiod of time at least as long as the stored time value, before thesystem indicates a malfunction so as to avoid unnecessary shutdown dueto transitory pressure fluctuations.

In the exemplary logic flow the control circuit monitors the fluidpressure signal from the sensor 496 as represented in a step 574. Instep 576 a determination is made whether the pressure signal correspondsto a pressure above the minimum pressure. If the pressure is at or belowthe lower pressure limit value a timing function responsive to timer 460is carried out in a step 578. The control circuit continues to operateand determine in a step 580 if the pressure signal corresponds to apressure at or below the lower limit for longer than the pressure timevalue. If the low-pressure condition has persisted for at least thepressure time value, an indication of the condition is given at a step582 and the clutch is disengaged in a manner like that previouslydiscussed.

In some exemplary systems a high-pressure condition from the pump 472may sometimes occur. This may happen for example in the event that thereis a blocked line, a clogged filter or other malfunction. In theexemplary embodiment the data store 462 includes data corresponding toan upper pressure limit value. This upper pressure limit value isindicative of such a malfunction.

As represented in step 584 control circuit operates to monitor thepressure signal to determine if the pressure signal corresponds to apressure at or above the upper pressure limit value. If so the controlcircuit operates to indicate the condition as represented in the step586 and disengages the clutch in a manner previously discussed. If thepressure is within limits, the logic then proceeds to a step 588 inwhich the temperature signal from sensor 494 is monitored.

As previously discussed, data stored in data store 462 includes clutchtemperature limit values. One of these values is a disengagement limitvalue. This value corresponds to a temperature that if reached is deemedunreasonably high and represents a condition in which the clutch shouldno longer be operated. In the exemplary arrangement the disengagementvalue is higher than the re-engagement limit temperature valuepreviously discussed, which the temperature must be below before theclutch will change from a disengaged condition to an engaged condition.

As represented in step 590 the temperature monitored in step 588 isevaluated to determine if it is at or above the level of thedisengagement limit value stored in the data store. If the temperatureis above the disengagement value the control circuit operates toindicate the condition in a step 592. In the exemplary arrangementbecause this condition represents a serious malfunction, the controlcircuit is operative to set a lockout status in step 594. In theexemplary embodiment the lockout status is set for a lockout time valuewhich is a value stored in the data store in association with theparticular condition. Thus for example in some exemplary arrangementsthe detection of a high temperature condition may be associated with alockout value that prevents the clutch from being reengaged for a timeperiod of 15 minutes, which corresponds to the stored value based onprogramming that considers this time sufficient for reasonable cooldown.Of course these values are merely exemplary in other embodiments otherapproaches and values may be used.

If the fluid temperature is found to be within normal operating limitsin step 590 the control logic proceeds to a step 596. In the exemplarystep 596 the control circuit operates to determine if the valve 476 isoperating properly. For example in some exemplary embodiments the valvemay operate in response to pulse width modulated signals. In thisexemplary step the control circuit operates to determine if the pressureoutput supplied by the valve or the position of components within thevalve, properly correspond to the signals that the valve is receiving.Of course this is merely exemplary of ways in which signals from thevalve may be utilized for purposes of determining if the valve isoperating properly.

If in step 598 it is determined that the valve is not operating properlythe control circuit operates to give an indication thereof in a step600. Because a valve malfunction is considered to be a serious conditionwhich may present the possibility for damage to the driving or drivendevices, the condition causes the control circuit to set a lockout suchas through step 594 previously discussed. This lockout condition may beof a duration different than the lockout previously discussed or may beof the same duration. Alternatively or in addition a lockout mayadditionally require a reset or replacement of certain system componentsbefore operation will again occur. The programming of the particularsystem will depend on the requirements associated with the particularfunctions and operations that are being carried out.

The exemplary control logic further carries out a step 602 in which thecontrol circuit monitors for signals that correspond to an instructionto stop or otherwise discontinue operation of the driven device. Thismay include for example an operator pushing an emergency stop button.Alternatively or in addition this may correspond to triggering of asafety switch that indicates a potential problem. The exemplarycircuitry monitors for the occurrence of such condition or receipt ofsuch a signal in a step 604. If such a signal is received an indicationof the condition is provided in a step 606 and the clutch is disengaged.Otherwise the logic proceeds.

In the exemplary arrangement the control circuit is operative to monitorfor conditions which may correspond to operational problems. For thesereasons the input speed signal and output speed signal are monitored inthe exemplary embodiment to detect malfunctions or other conditions thatmay arise. In order to assure that the control circuit can detect theseconditions, the control circuit operates to monitor for the presence ofthe input speed signal indicative of the speed of the driver device at astep 608. If the input speed signal has been determined to have beenlost at a step 610 an indication thereof is given in a step 612 and theclutch is disengaged and shut down. The output speed signal indicativeof the speed of the driven device is also monitored in a step 614. If itis determined in the step 616 that the output speed signal has beenlost, an indication is given in a step 618 and the clutch disengaged andshut down.

In the exemplary logic flow, the control circuit is operative to monitorthe amount of slip that is occurring in the clutch. The clutch sliplevel may be indicative of problems such as an overload condition or aclutch wear condition that adversely impacts system operation and whichmay cause problems. In the exemplary arrangement the data store 462includes data corresponding to a maximum slip level value, an engagementtime value, and a maximum slip duration value. In the exemplaryembodiment the stored values are used to identify conditions whichrepresent an unacceptable amount of clutch slippage. In the exemplaryarrangement if the clutch slippage level exceeds the stored maximum sliplevel value for period of time that is equal to the stored engagementtime value, then the control circuit operates to increase the level ofpressure applied to the piston cavity by the valve to increase the axialforce on the disc pack. Often increasing of the axial force on the discpack will reduce the level of slippage. However in the exemplaryarrangement if increasing the axial force does not reduce the slippagelevel and the slippage level continues to be over the maximum slip levelvalue for at least a period of time corresponding to the maximum slipduration value, then the clutch is disengaged and a lockout is set.

This exemplary logic is represented beginning with a step 618. In step618 the control circuit is operative to determine the slip level of theclutch based on the difference between the speeds represented by theinput speed signal and the output speed signal. In a step 620 adetermination is made whether the determined slip level is greater thanor equal to the stored maximum slip level value. If the slip levelexceeds the stored value a timing function responsive to timer 460 isinitiated at a step 622. In a step 624 the control circuit uses thetimer to determine if the elapsed time has reached the level of theengagement time value stored in the data store. If the time does notcorrespond to the engagement time value, it is determined if the timecorresponds to a time greater than the stored maximum slip durationvalue. This is represented in a step 626.

Until the time of the engagement time value is reached, the controllogic continues to monitor the slip level without changing the system.If before a time duration corresponding to the engagement time value,the determined slip level falls below the stored maximum slip levelvalue, the logic proceeds and no additional action is taken. This mightoccur for example if the driven device temporarily has a brief spikeloading condition. However if the determined slip level is greater thanor equal to the stored maximum slip level value for a time that is equalto the stored engagement time value, the control circuit carries outstep 628 in which the valve 476 is operated to increase the amount ofpressure that is applied to the piston cavity to compress the disc pack.

If the step of increasing the pressure on the disc pack in step 628reduces the slippage to a level below the maximum slip level value, thepressure is maintained for a programmed time period and then returnedback to the initial pressure value. However if the calculated slip levelas determined in step 620 continues to be above the stored maximum sliplevel value continuously for a time that corresponds to the maximum slipduration value, the control circuit then operates in a step 630 toindicate the condition, set a lockout status in a step 632, anddisengage and shut down the clutch. Of course it should be understoodthat this approach is exemplary and other embodiments other approachesmay be used. Further such features may be used to monitor and adjustclutch slippage in systems where slippage is varied to control outputspeed such as certain systems previously discussed herein.

If in the step 620 the slip level is determined to be within limits, thelogic flow proceeds to a step 634. In step 634 control circuit isoperative to read the at least one coupling status signal from thecoupling status sensors such as sensors 446 and 448. As represented in astep 636 a determination is made that the coupling status signals arepresent. In the event of that the coupling status signals are notdetected as present the control circuit indicates the condition in astep 638 and disengages the clutch in a manner previously discussed.

In the exemplary embodiment the at least one data store 462 associatedwith the control circuit 456 includes data corresponding to at least onecoupling status value. In the exemplary arrangement the at least onecoupling status value corresponds to a lag value which represents theamount by which the inner portion 434 of the coupling lags behind themovement of the outer portion of the coupling 432. In the exemplaryarrangement the control circuit operates to receive the coupling statussignals which correspond to the current deformation of the resilientbodies 442 of the coupling. Based on the stored coupling status valueand the coupling status signals the control circuit makes a couplingstatus determination. In the exemplary arrangement this determination isbased on the determined lag in rotational movement of the inner portionof the coupling relative to the outer portion of the coupling. In theexemplary arrangement the stored coupling status value corresponds to amaximum amount of acceptable lag between the outer and inner couplingportions beyond which is indicative of a malfunction.

As represented in step 638 the control circuit is operative to calculatethe lag between the inner and outer coupling portions. In a step 640 thecontrol circuit is operative to determine if the calculated lag isgreater than or equal to the coupling status value stored in the datastore 462. If the calculated lag value exceeds the stored maximumthreshold this is indicative of a problem which warrants a systemshutdown. In response to detecting this condition the control circuit isoperative to indicate the condition at a step 642 and to set a lockoutstatus as represented in step 644. The control circuit then carries outclutch disengagement and shut down in the manner previously discussed.Of course this approach is exemplary and other embodiments otherapproaches may be used.

In exemplary embodiments the control circuit further monitors for anoverload condition. Such an overload condition may correspond to thedriven device applying an excessive load that may be damaging to theclutch, the driver device or other system components. In exemplaryembodiments the load that is applied by the driven device is indicatedby the load signals that are received from the at least one sensor 500.As previously discussed these loads signals may come from the electroniccontrol module associated with the engine or other sensors associatedwith the system. The exemplary data store 462 includes stored datacorresponding to at least one overload value. This overload valuerepresents a loading which is potentially damaging to the systemcomponents and therefore if encountered represents a system malfunctionwhich warrants a system shutdown.

In the exemplary embodiment the control circuit is operative to monitorthe at least one load signal as represented in a step 646. In a step 648a determination is made whether the load signal is present. If the loadsignal has been lost an indication thereof is provided in a step 650. Inresponse to loss of the load signal, the clutch is disengaged and ashutdown is carried out as previously discussed. If the load signal ispresent then a determination is made in a step 652 concerning whetherthe load signal is equal to or greater than the stored overload value.If the load signal indicates that the load is greater than the overloadvalue, the control circuit is operative to indicate the condition in astep 654. A lockout status is then set at a step 656. As previouslydiscussed the lockout status may be associated with a stored time valuethat corresponds to the particular condition or may be determined inanother manner through operation of the control circuit. The lockoutstatus may further require that certain actions be taken to restore thesystem to operation. Thereafter the clutch is disengaged and shut downas previously discussed.

As represented in the schematic logic flow, the logic returns tocontinuously monitor for conditions that may require a change in thesystem operation. The logic flow is carried out until a change in one ofthe conditions occurs which then results in disengagement of the clutchby the control circuit operating the valve. Of course it should beunderstood that this simplified control logic is merely exemplary and inother embodiments other approaches, functions and capabilities may beprovided.

FIG. 47 shows a partial cross-sectional view of an alternativeembodiment of a fluid actuated clutch 658. Clutch 658 is configured toprovide enhanced vibration damping capabilities which are integratedwith structures in the clutch rather than provided through an externalcoupling device as described in connection with the previousembodiments. The exemplary clutch 658 includes a disc housing 660. Thedisc housing is configured to be in operative connection with the driversuch as a flywheel of an engine or other rotatable driving device. Theclutch is in operative connection with a shaft 662. The shaft isrotatable about an axis 663. The shaft is configured to be in operativeconnection with a rotatable load of the types previously discussed. Ofcourse it should be appreciated that this arrangement is exemplary andthat in some embodiments the operative orientation may be reversed suchthat the shaft is in direct connection with the driver and the dischousing is in direct connection with a load.

In the exemplary arrangement the clutch 658 includes a disc pack 664.The disc pack includes a plurality of clutch discs 666 which arealternatively referred to as friction discs. The disc pack furtherincludes a plurality of separator discs 668. Each separator disc ispositioned in axially intermediate relation between an immediatelyadjacent pair of clutch discs. Each of the clutch discs includes aplurality of angularly spaced splines 670 that extend at the outerperiphery of each clutch disc. The clutch disc splines extended ininterengaging relation with an inner annular splined surface 672 of thedisc housing 660. In the exemplary arrangement the annular splinedsurface 672 includes a plurality of angularly spaced, radially inwarddirected axially elongated ring splines 674. In the exemplaryarrangement the clutch discs are enabled to move axially relative to thedisc housing 660 while remaining in engagement with the ring splines674.

The exemplary clutch 658 further includes an annular hub 676. The hubextends in surrounding relation of a tapered forward portion of theshaft 662. The hub includes an annular outward splined portion 678. Thehub splined portion includes a plurality of angularly spaced axiallyelongated radially outward directed hub splines 680, similar to thosepreviously discussed. Each of the separator discs 668 include an innerannular splined separator surface 682. Each annular splined separatorsurface includes a plurality of angularly spaced radially inwardlydirected separator splines 684 which engage the hub splines 680 ininterengaging relation. As with the previously described embodiments theseparator discs 668 are axially movable relative to the hub 676 whilethe hub splines 680 and the separator splines 684 remain ininterengaging relation.

The exemplary disc pack 664 is bounded at an inward end of the shaft bya backplate 686. The backplate 686 is in attached connection with thehub 676 through a plurality of fasteners 688. A lock ring 690 isattached to the inward end of the shaft and operates to prevent movementof the hub 676 relative to the shaft. Of course it should be understoodthat this approach is exemplary and in other embodiments otherapproaches may be used.

The exemplary clutch includes a cylinder 692. The cylinder 692 includesa housing 694. The cylinder 692 further includes an annular piston 696.The piston 696 is axially movable relative to the housing 694. Thepiston 696 and the housing 694 bound a variable volume cavity 698. Thecavity changes volume responsive to the delivery of fluid thereto andthe release of fluid therefrom. A fluid passage 700 is in operativeconnection with a source of fluid, the delivery and release of which iscontrolled by a valve or other control device. A plurality of seals 702are operative to maintain the cavity 698 in fluid tight relation duringrelative movement of the housing 694 and the piston 696. In someexemplary arrangements the fluid that is delivered at high pressure tothe cavity 698, may comprise a gas such as compressed air, while inother embodiments the fluid may comprise a liquid such as hydraulicfluid.

In the exemplary arrangement the housing 694 of the cylinder 692 isrelatively rotatably mounted through an outboard bearing 704 to acylindrical portion 706 of the hub 676. The piston 696 is relativelyrotatably mounted through an inboard thrust bearing 708. The thrustbearing 708 extends in surrounding relation of a push ring 710. The pushring 710, which is alternatively referred to herein as a pressuresleeve, is axially movable on the cylindrical portion 706.

The push ring 710 is in operative connection with a pressure plate 712.The pressure plate 712 axially outwardly overlies the disc pack 664. Asa result in the exemplary arrangement when fluid is delivered into thecavity 698 the volume of the cavity expands and the annular piston 696moves axially away from the housing 694 and toward the disc pack. Thepiston causes axial movement of the thrust bearing 708 and the push ring710 relative to the cylindrical outer surface of the cylindrical portion706. Axial movement of the push ring 710 toward the disc pack 664 causesmovement of the pressure plate 712 which compresses the clutch discs andthe separator discs in the disc pack in a manner like that previouslydiscussed. The compression of the clutch discs and the separator discscauses the rotational movement of the driver which is attached to thedisc housing 660, to be transmitted through the disc pack and to rotatethe shaft 662 and the load of the driven device attached thereto in amanner like that previously discussed. The release of fluid pressurefrom the cavity 698 causes the volume of the cavity to decrease. This inturn causes the piston 696, the push ring 710 and the pressure plate 712to axially move in a direction away from the disc pack and/or to relievethe compressive force acting on the disc pack. The release of thecompressive force enables the disc housing 660 to rotate independentlyof the shaft 662. Of course it should be understood that this clutcharrangement is exemplary and in other embodiments other clutcharrangements may be used.

In the exemplary clutch 658 the cylinder and the disc pack arepositioned in a bell housing 714. The bell housing includes a flangeportion 715. As shown in FIG. 48 the exemplary flange portion 715includes a plurality of openings 716. The openings 716 of the exemplaryembodiment are configured to accept fasteners such as bolts therethroughfor purposes of connecting the bell housing to an engine block or otherhousing structure of the driver.

The disc housing 660 of the exemplary clutch 658 includes a plurality ofangularly spaced engagement projections or openings 718. In exemplaryarrangements the engagement projections or openings are configured toreleasably engage a rotatable member of the driver such as a flywheel.In some exemplary arrangements the disc housing may include a pluralityof projections or studs that extend in openings in the flywheel or otherdriving member to transmit rotational force to the disc housing. Inother exemplary arrangements openings in the disc housing may receivebolts or other releasable fasteners that extend into engagement with theflywheel or other driving member so as to transmit force therefrom. Instill other exemplary arrangements the disc housing may include bothprojections and openings for receiving releasable fasteners therein thatare operative to releasably connect the disc housing and a drivingmember. Of course it should be understood that these approaches areexemplary and other embodiments other approaches may be used.

In the exemplary clutch 658, the bell housing 714 is in releasableconnection with a bearing housing 720. The bearing housing 720 of theexemplary arrangement houses a pair of axially disposed tapered rollerbearings 722, 724. The bearings 722 724 are configured to prevent axialmovement of the shaft 662 relative to the clutch. In the exemplaryarrangement bearing 724 is in abutting engagement with a radiallyoutward annularly directed step 726 of the shaft 662. Bearing 722 is inabutting engagement with a stop ring 728 which is in abutting engagementwith the cylindrical portion 706 of the hub 676. Thus as can beappreciated the bearings and the bearing housing help to maintain theshaft 662 in the proper position relative to the clutch components. Ofcourse it should be understood that this configuration is exemplary andother embodiments other approaches may be used.

The exemplary disc housing 660 of clutch 658 is constructed so as toprovide vibration damping capabilities. The exemplary disc housing 660is constructed so as to provide the vibration damping capabilities in asize envelope having an axial length that is substantially the same asthat required of a conventional disc housing. This enables the exemplaryarrangement to have a more compact structure and to fit more readilywithin limited spaces where it may otherwise be difficult to incorporatea vibration damping device. As shown in FIG. 40 the exemplary dischousing 660 includes an inner annular housing ring 730 and outer annularhousing ring 732. The inner annular housing ring of the exemplaryarrangement comprises a continuous annular ring that includes the innerannular splined surface 672 with the axially elongated angularly spacedring splines 674. The exemplary inner housing ring 730 further includesa plurality of angularly spaced radially outwardly directed inner ringprojections 734. Each inner ring projection 734 includes a pair ofangularly disposed radially extending inner ring projection sidewalls736. Each inner ring projection is bounded radially outwardly by aninner ring projection top wall 738 which extends transversely betweenthe inner ring projection sidewalls 736. In the exemplary arrangementeach of the plurality of inner ring projections extend a majority of theaxial width of the inner housing ring 730. In the exemplary arrangementan inboard arcuate portion 740 of the inner housing ring 730 extendsinboard of each inner ring projection 734, and each inner ringprojection extends substantially flush with the outboard face 742 of theinner drive ring. An arcuate outer segment 744 extends at a radiallyouter surface of the inner housing ring in areas angularly between eachof the inner ring projections 734. Of course it should be understoodthat this configuration is exemplary and in other embodiments otherapproaches may be used.

The exemplary outer housing ring 732 includes a plurality of angularlyspaced outer ring projections 746. The outer ring projections eachinclude a pair of radially extending outer ring projection sidewalls748. Each outer ring projection 746 is radially inwardly bounded by anouter ring projection bottom wall 750 that extends transversely betweenthe outer ring projection sidewalls 748. In the exemplary arrangementthe outer ring projections 746 are connected through a continuousannular outer housing ring portion 752. The outer housing ring portionis configured to radially outwardly overlie the inboard arcuate portions740 of the inner housing ring when the inner and outer housing rings arein the assembled condition.

In the exemplary arrangement each of the outer ring projections 746 isconfigured to extend angularly intermediate of each pair of immediatelyadjacent inner ring projections 734 on the inner housing ring 732.Further in the exemplary arrangement each of the outer ring projections746 includes a respective one of the engagement projections or openings718 therethrough. The projections or openings enable the exemplary outerhousing ring 732 to be releasably engaged in fixed attached connectionwith the flywheel or other rotatable member of the driver or load.

In the exemplary arrangement each of the outer ring projection sidewalls748 include a pair of nesting recesses 754. In the exemplary arrangementeach of the nesting recesses 754 are spaced from one another in adirection parallel to the axis in an outer ring projection sidewall 748.Each nesting recess extends substantially perpendicular to the radialdirection. Further in the exemplary arrangement the outer ringprojection sidewalls 748 on each angular side of each outer ringprojection 746, include a pair of nesting recesses 754.

The exemplary inner housing ring 730 further includes a pair of axiallydisposed nesting recesses 756 in each inner ring projection sidewall 736of each inner ring projection 734. Each nesting recess 756 of theexemplary embodiment extends substantially perpendicular to the radialdirection. In the exemplary embodiment when the inner housing ring andthe outer housing ring are in the operative position each nesting recess756 in a respective inner ring projection sidewall 736 is in alignedfacing relation with the corresponding nesting recess 754 in animmediately adjacent facing outer ring projection sidewall 748. Furtherin the exemplary arrangement the outer ring projection bottom walls 750and the radially inward continuous outer housing ring portion 752 areradially disposed away from the arcuate outer segments 744 and inboardarcuate portion 740 such that the outer housing ring 732 and the innerhousing ring 730 are relatively rotationally movable.

As shown in FIGS. 50-54 the exemplary disc housing 660 in assembledcondition includes a plurality of deformable resilient bodies in theform of resilient blocks 758. In the exemplary arrangement the resilientblocks 758 include in transverse axial cross-section, radially extendingangularly disposed block sidewalls 760. Each block sidewall 760 of theexemplary embodiment is in abutting engagement with one of theimmediately adjacent inner ring projection sidewalls 736 or outer ringprojection sidewalls 748. In the exemplary arrangement the deformableresilient blocks are comprised of rubber, elastomer or other deformableresilient material and operate to resist relative rotational movement ofthe inner housing ring 730 and the outer housing ring 732. In theexemplary arrangement the resilient blocks 738 further operate asresilient spacers that extend radially intermediate of the arcuate outersegment surface 744 of the inner housing ring 730 and the immediatelyadjacent outer ring projection bottom wall 750 of the outer housing ring732.

As can be appreciated in the exemplary arrangement the deformableresilient blocks 758 provide a resilient deformable connection betweenthe inner housing ring 730 and the outer housing ring 732. Thisdeformable resilient connection is operative to absorb and dampenvibration, shock and transient forces that may be imparted to the outerhousing ring 732 by the flywheel or other rotating member of the driver.In some exemplary arrangements the block sidewalls 760 may be fastenedor adhered to the adjacent inner ring projection sidewalls 736 and outerring projection sidewalls 748 by adhesives or other fastening methods toassure that the resilient blocks remain in position. Further theexemplary resilient blocks 758 include in axially transversecross-section a bottom central projection 762. In exemplary arrangementsthe bottom central projection 762 is operative to abuttingly engage thearcuate outer segment 744 immediately underlying the resilient block 758as shown in FIG. 55. In some exemplary arrangements this configurationmay facilitate the relative rotational movement of the inner and outerhousing rings while preventing radial movement as well as preventingdeformation of corner areas of the resilient blocks which may twist orotherwise cause interference with such relative movement. Of course itshould be understood that this configuration is exemplary and otherembodiments other configurations may be used.

In alternative arrangements the disc housing may utilize a resilientbody comprising resilient blocks 764 shown in FIG. 54 in place of theresilient blocks 758. The resilient blocks 764 have a generally similarsidewall profile to the resilient blocks 758 discussed. However in theexemplary arrangement the resilient blocks 764 have a different profilefrom blocks 758 in axially transverse cross-section which may be usefulin certain arrangements in providing damping properties and or inattenuating certain frequencies or other conditions. Further in otherexemplary arrangements other sizes and configurations of deformableresilient blocks or bodies may be utilized.

FIGS. 56-59 show an alternative disc housing arrangement 766. Dischousing 766 is the same as disc housing 660 except for the deformableresilient bodies used therewith. Disc housing 766 includes the innerhousing ring 730 and the outer housing ring 732 previously discussed.However extending between each immediately angularly adjacent inner ringprojection sidewall 736 and outer ring projection sidewall 748 extends adeformable resilient element 768 shown in FIG. 59. Deformable resilientelement 769 includes a block 770 that is generally similar incross-section to resilient block 758 previously discussed. However apair of compression springs 772 extend through the block 770. Thesprings 772 are spaced parallel to the axial direction and extendparallel to one another. The end portions of each spring 772 extendoutward from the angularly disposed sidewalls 774 of the block 770. Eachend portion of a respective spring 772 extends in a respective nestingrecess 754, 756. The respective ends of the springs 772 being engaged inrespective nesting recesses helps to hold the deformable resilient bodyelement 768 in engaged relation between the inner ring projectionsidewalls 736 and outer ring projection sidewalls 748. Further in thisexemplary arrangement the combination of the resistive force provided bythe combination of the springs 772 and the resilient block 770 providedifferent damping capabilities that may be tailored to particular speedsor other conditions of the particular clutch implementation.

FIG. 60 shows an exemplary clutch 776. Clutch 776 is substantially thesame as clutch 658 previously described. However clutch 776 includesdisc housing 766. As can be appreciated the exemplary disc housing 766provides vibrational damping and shock attenuation capabilities that maybe varied through the resilient properties of the block 770 and thecompression springs 772 so as to achieve properties that are bettersuited for the particular environment and driver that is utilized. Ofcourse it should be understood that this arrangement is exemplary andthat in other embodiments other approaches may be used.

FIGS. 61-64 show an alternative disc housing 778. Disc housing 778 isthe same as disc housings 660 and 766 previously discussed other thanthe deformable resilient elements that extend operatively between theinner housing ring 730 and the outer housing ring 732 to resist relativerotational movement thereof. In the exemplary disc housing 778 thedeformable resilient bodies include compression springs 780 as shown inFIG. 64. In this exemplary arrangement a compression spring 780 extendsbetween each pair of immediately adjacent nesting recesses 754, 756.Thus as shown in FIGS. 61 and 62 in this exemplary arrangement twocompression springs 780 extend between each immediately adjacent innerring projection sidewall 736 and outer ring projection sidewall 748. Aswill be appreciated by those skilled in the art, the spring diameter,material and spring rates of springs 780 may be varied to achievedesired vibration damping capabilities as necessary for the particulardriver and application in which the disc housing 778 is utilized.

Further in some alternative exemplary arrangements disc housing 778 mayfurther include resilient spacers 779 that extend arcuately betweenimmediately angularly adjacent sidewalls 736 of immediately adjacentinner ring projections 734. In some exemplary embodiments the resilientspacers extend radially intermediate of the arcuate outer segment 744between the inner ring projections and the outer ring projection bottomwall 750 of the outer ring projection 746 intermediate of the adjacentinner ring projections. In this exemplary alternative arrangement theresilient spacers 779 comprise a plurality of deformable resilient padswhich extend radially between each arcuate outer segment 744 and outerring projection bottom wall 750. In alternative arrangements suchdeformable resilient spacers may provide additional vibration dampingand other properties between the relatively movable inner housing ring730 and outer housing ring 732.

FIGS. 65 through 68 shows yet another alternative embodiment of a dischousing 782. The exemplary disc housing 782 is similar to the dischousings previously discussed and in the exemplary arrangement includesthe same inner housing ring 730 and outer housing ring 732. Disc housing782 includes a plurality of resilient deformable elements comprisingpairs of nested springs generally indicated 784 in FIG. 68. In theexemplary arrangement the nested springs include an outer spring 786which has an internal opening therethrough that is sized to accept theinner spring 788 therein. The combined nested springs 784 provide acombined spring rate of both the inner spring 788 and the outer spring786. The combined springs further provide a different damping and shockabsorption capabilities from the single compression springs 780 used indisc housing 778. Thus disc housing 782 can be tailored to conditionsand made suitable for use in other types of applications.

FIGS. 69-72 show a further disc housing 790. Disc housing 790 is similarto disc housings 600, 766, 778 and 782 previously discussed and differsonly in the deformable resilient elements that are utilized. In dischousing 790 a pair of axially spaced compression springs 792 extend inaligned nesting recesses 754, 756 of the inner housing ring and theouter housing ring in a manner similar to that described in connectionwith disc housing 778. However, disc housing 790 further includes aseparate additional compression spring 794. Compression spring 794 ispositioned axially intermediate of each of immediately adjacent pair ofsprings 792. This exemplary arrangement provides the capabilities fordifferent combinations of spring sizes and spring rates to producedifferent types of vibration damping properties which may be tailored tothe particular clutch environment.

FIGS. 73 through 77 show an alternative arrangement of a disc housing796. Disc housing 796 includes an inner housing ring 798 and an outerhousing ring 800. Similar to inner housing ring 730 previouslydescribed, inner housing ring 798 includes an inner annular splinedsurface 802 that includes a plurality of angularly spaced, axiallyelongated ring splines 804 that are configured for engaging clutch discsplines that extend at the outer periphery of clutch discs.

The exemplary inner housing ring 798 further includes a plurality ofangularly spaced radially outward extending inner ring projections 806.The inner ring projections are bounded on each angular side by radiallyextending inner ring projection sidewalls 808. An inner ring projectiontop wall 810 outwardly radially bounds each inner ring projection andextends transversely between the inner ring projection sidewalls.Arcuate outer segments 812 extend angularly between each of the innerring projections 806. An inboard arcuate portion 814 extends on theinner housing ring 798 inboard of each inner ring projection 806.

The exemplary outer housing ring 800 includes a plurality of angularlyspaced radially inward directed outer ring projections 816. Each outerring projection 816 includes a pair of angularly disposed radiallyextending outer ring projection sidewalls 818. An outer ring projectionbottom wall 820 radially inwardly bounds the outer ring projection andextends transversely between the outer ring projection sidewalls. Eachouter ring projection bottom wall includes an angularly enlarged portion824 at the inboard end. The angularly enlarged portion 824 extends inradially outwardly spaced overlying relation of the correspondinginboard arcuate portion 814 of the inner housing ring 798 when the dischousing 796 is in the assembled operative condition.

The exemplary outer housing ring 800 further includes a plurality ofengagement projections or openings 826. Engagement projections oropenings are utilized in a manner similar to engagement projections oropenings 718 in the outer housing ring 732 and may be used to releasablyoperatively connect outer housing ring 800 at its inboard side to aflywheel or other rotating member of the driver. In addition theexemplary outer housing ring 800 includes a plurality of attachmentopenings 828. Attachment openings 828 may be used in some exemplaryarrangements for purposes of attaching an annular cover piece or othersimilar structure to the outer housing ring 800. Such a annular covermay be useful in preventing material that is worn from deformableresilient bodies from escaping from the area intermediate of the innerhousing ring and the outer housing ring. Of course these approaches areexemplary and other embodiments other approaches may be used.

In the exemplary arrangement the inner ring sidewalls 708 and the outerring sidewalls 818 include in axially transverse cross sectionrespective semicircular recesses 830, 832. In the exemplary arrangementthe semicircular recesses are elongated in a direction parallel to theaxis. The combined semicircular recesses 830, 832 are configured to formcylindrical pockets 834 between immediately angularly adjacent innerring sidewalls 808 and outer ring sidewalls 818.

The exemplary cylindrical pockets 834 are configured to receive thereindeformable resilient bodies which in disc housing 796 are comprised ofresilient tubes 836 shown in FIG. 77. In the exemplary arrangement theresilient tubes are elongated along a tube axis 838. The resilient tubes836 further include in axially transverse cross-section a positioningprojection 840 that extends radially outward relative to the tube axis.The positioning projections 840 of the exemplary arrangement in anoperative position in the disc housing extend radially outwardly andmaintain the resilient tubes 836 in a fixed rotational position andresist twisting and rotational movement thereof in the cylindricalpockets 834. Of course this approach is exemplary and other embodimentsother approaches may be used.

In exemplary arrangements the resilient tubes 836 may be comprised ofdeformable material such as an elastomer or rubber material. In otherarrangements the resilient tubes may have a deformable resilient coverand include an internal chamber that houses a compressible orincompressible material. Such compressible or incompressible materialmay comprise a gas, liquid or gel so as to provide suitable compressiveand resilient properties for the resilient tubes 836. As previouslydiscussed, by changing the resilient properties of the tubes 836 thedamping properties achieved through the relatively rotationally movableinner housing ring 798 and outer housing ring 800 may be varied andtailored to the particular operating conditions of the drive system inwhich the disc housing 796 and clutch are utilized.

FIG. 78 shows an alternative clutch 842. Clutch 842 is generally similarto clutch 658 previously described. However clutch 842 includes acylinder 844 that is supplied with actuating fluid pressure through afluid passage 846 that extends through a shaft 848. In exemplaryarrangements the fluid passage 846 may be selectively supplied orrelieved of actuating fluid for the clutch cylinder 844 through a clutchactuation coupling like coupling 64 previously discussed, or anothersuitable fluid connection arrangement.

The exemplary clutch 842 further includes an axially movable piston 850that operates to axially compress a disc pack 852 through a pressureplate 854. The disc pack 852 extends between the pressure plate 854 anda back plate 856. Exemplary clutch 842 includes a hub 858 which engagesthe separator plates of the disc pack 852 and a disc housing 860 that issimilar to disc housing 766 previously discussed. The exemplary discpack further includes a plurality of release springs 862 that extendparallel to the axis 864 of the shaft 848. The springs 862 comprisecompression springs which facilitate the separation of the clutch discsand the separator discs of the disc pack when fluid is released from thevariable volume cavity 866 of the clutch that is in operative connectionwith the fluid passage 846.

Clutch 842 includes a bell housing 868 that at the inboard end is inoperative connection with an engine block or other housing 870 which isshown in phantom. Likewise the disc housing 860 is shown in operativeconnection with a flywheel 872 of an engine or other driver. As can beappreciated the exemplary clutch 842 with the disc housing 860 includingthe deformable resilient bodies thereof provides vibration damping andattenuation capabilities that are suitable for the particular clutch anddrivetrain environment.

In further exemplary arrangements vibration damping and attenuationcapabilities may be achieved or improved through the use of vibrationdamping separator discs that are utilized in connection with a clutchdisc pack of the types previously discussed. Such exemplary vibrationdamping separator discs may provide further vibration attenuation andcontrol of vibration properties within the clutch without therequirement for additional axial space within the disc pack or the driveline.

FIGS. 79 through 82 show an exemplary embodiment of a vibration dampingseparator disc 874. The exemplary separator disc includes an inner ring873 with an annular splined separator inner surface 876 which includes aplurality of angularly spaced inwardly directed separator splines 878.Splines 878 are configured in a manner like that previously discussedand interengage with outwardly directed axially elongated hub splines ofa hub of clutch. In the exemplary arrangement each separator disc isoperative to transmit rotational force between the immediately axiallyadjacent clutch discs and the hub of the clutch when the clutch isengaged while providing vibration damping capabilities.

As shown in FIG. 82 the exemplary separator disc 878 includes a centraldisc piece 880. The central disc piece includes the inner ring 873 withannular splined inner surface 876. The central disc piece 880 furtherincludes a plurality of angularly spaced radially outward extendingposts 882. The exemplary post 882 extend outward from a radially outerface 884 of the inner ring 873 and terminate radially outwardly at anenlarged outward end 886.

The exemplary separator disc 878 further includes a pair of opposedouter disc pieces 888, 890. Outer disc pieces 888 and 890 extend onopposed axial sides of central disc piece 880. In the operativeposition, each outer disc piece includes a plurality of angularly spacedradially inward extending projections 892. Projections 892 arecorrespondingly spaced on each of the outer disc pieces 888, 890 so thatthe projections are in abutting relation in the assembled condition ofthe separator disc. Each of the projections 892 are positioned angularlyintermediate of the posts 882 on the central disc piece. Each outer discpiece further includes an annular projecting portion 894. Each annularprojecting portion includes openings 896.

In the exemplary arrangement the separator disc 878 includes a pluralityof angularly spaced separator compression springs 898. When the centraldisc piece 880 and the outer disc pieces 888 and 890 are assembled, thecentral disc piece is relatively rotationally movable with respect tothe outer disc pieces. A separator spring 898 extends transverselyintermediate of each immediately angularly adjacent post 882 and theangularly aligned abutting projections 892 of the outer disc pieces 888,890. Each separator spring 898 further extends in the openings 896 inthe annular projecting portion 894 of each outer disc piece. As a resulteach separator spring 898 is held in intermediate relation between eachpost 882 and the aligned projections 892, is further held in position byextending in the openings 896 and is held radially inwardly by theenlarged outward ends 886 of the posts. The outer disc pieces 888, 890and the central disc piece 880 are held in engaged relation through aplurality of angularly spaced rivets 900 which extend through respectiveopenings 902, 904 in the outer disc pieces. Further in the exemplaryarrangement a plurality of elastic spacers 906, 908 are positioned tohold the separator springs 898 movably positioned between the outer discpieces. Further in the exemplary arrangement of separator disc 874 theannular projecting portions 894 of the disc pieces include a pluralityof angularly spaced circular recesses 910. The recesses 910 which arepositioned angularly intermediate of the separator springs 898 and whichcorresponds to the projections 892, are configured to position releasesprings such as springs 862 previously discussed, that serve to separatethe separator discs and clutch discs from engagement when the clutch isdisengaged.

In this exemplary arrangement of the separator disc 874, the separatorsprings 898 serve as deformable resilient, components that arepositioned operatively intermediate of the outer disc pieces 888, 890and the central disc piece 880. In this exemplary arrangement the outerdisc pieces which are held together by the rivets 900 are relativelyrotationally movable with respect to the central disc piece 880. Thedeformable resilient separator springs 898 are operative to resistrelative movement of the central disc piece and the outer disc pieces.Thus in this exemplary arrangement of the separator disc 894 thedeformable resilient springs are operative to absorb vibrational andtransient forces through deformation in a manner similar to the dischousings previously discussed so as to reduce vibration effects.

FIGS. 83 through 86 show an exemplary disc pack 912 which includesseparator discs 874. The separator discs are positioned in the disc packintermediate of clutch discs 914 which may be of the type previouslydiscussed. The disc pack extends between a backplate 916 and a combinedpressure plate and piston 918. The exemplary disc pack further includesa plurality of axially extending release springs 920. Springs 920 biasthe separator discs 874 apart to help disengage the clutch discs in theseparator discs when actuating fluid pressure to the clutch is released.

FIG. 87 shows an exemplary embodiment of a clutch 922. Clutch 922 isgenerally similar to clutch 842 that was previously discussed. Clutch922 includes the disc pack 912 including the separator discs 874. Inthis exemplary clutch 922 a disc housing 924 for the disc pack does notinclude the vibration damping and attenuating structures that areutilized in the clutch 842. Clutch 922 shows that in some exemplaryarrangements the vibration damping separator discs may be utilized inclutch arrangements without vibration damping disc housings. This mayinclude for example, existing clutch arrangements in which vibrationdamping separator discs are substituted for separator discs that do notinclude vibration damping features. Of course it should be understoodthat this arrangement is exemplary and in other embodiments otherapproaches may be used.

FIGS. 88-91 show a further alternative embodiment of a vibration dampingseparator disc 926. Separator disc 926 includes a central disc piece928. The central disc piece 928 includes an inner ring 929 with anannular splined separator inner surface 930 including a plurality ofangularly spaced inwardly directed separator splines 932. Separatorsplines 932 are configured for interengaging the outwardly directedsplines of a clutch hub in a manner like that previously discussed. Thecentral disc piece 928 includes an annular radially outward extendingdisc plate portion 934 that extends radially outward from the inner ring929. This plate portion 934 includes opposed central disc plate planarfaces 936 and 938.

An outer disc piece 940 extends on one axial side of the central discpiece 928 while an outer disc piece 942 extends on an opposed axialside. Each outer disc piece includes a pair of opposed planar faces 944and 946. A pair of planar elastic discs 948, 950 extend on opposed axialsides of the central disc piece 928. Elastic disc 948 extends axiallyintermediate and in abutting relation with planar face 946 or disc piece940 and central disc plate planar face 936 of the central disc piece928. Planar elastic disc 950 extends in abutting intermediate relationof planar face 946 of outer disc piece 942 and central disc planar face936 of central disc piece 928.

In the exemplary arrangement of separator disc 926, the outer discpieces 940, 942 are each relatively rotationally movable with regard tothe central disc piece 928 due to the intermediate planar elastic discs948, 950. In this exemplary arrangement the planar elastic discs providedeformable resilient components that are positioned operativelyintermediate of the central disc piece and the outer disc pieces whichserve to resist relative rotational movement of the central disc pieceand the outer disc pieces and thereby provide vibrational damping andshock attenuation within the clutch structure.

FIGS. 92 through 95 show an exemplary clutch disc pack 952 that includesthe exemplary separator discs 926. The exemplary separator discs arepositioned intermediate of clutch discs 954 which may be of the typepreviously discussed. Disc pack 952 extends between a backplate 956 anda combined pressure plate and piston 958 like that previously discussed.As in the previously discussed arrangement the pressure plate/piston 958is axially movable responsive to fluid that is supplied to a variablevolume cavity 960. The cavity 960 receives fluid from and releases fluidto an actuator fluid passage 962 that is in fluid connection with ashaft fluid passage similar to shaft fluid passage 846 previouslydiscussed.

FIG. 96 shows an exemplary clutch 964. Clutch 964 is generally similarto clutch 842 and clutch 922 previously discussed. Clutch 964 includes avibration damping disc housing 966 similar to disc housing 860. Clutch964 further includes a disc pack 968 that includes vibration dampingseparator discs 874. Of course it should be understood that disc pack968 may alternatively include vibration damping separator discs havingthe configuration of separator discs 926. Thus the exemplary clutch 964includes vibration damping and attenuation capabilities that areprovided in both the disc housing and the separator discs within theclutch structure. Thus as can be appreciated, clutch arrangements ofexemplary embodiments may provide multiple vibration damping andattenuating structures within the clutch and which can be configured toaddress the particular vibration damping and attenuating requirements ofthe particular clutch environment.

Although arrangements have been described based upon certain exemplaryembodiments, a wide array of modifications, variations and alternativeconstructions are also within the spirit and scope of the principlesdescribed herein. Example arrangements for mechanical clutches and otherrelated power transmission systems have been described herein withreference to particular components, features, properties, attributes,relationships and methods. However, it should be understood that inother embodiments other arrangements may include other components,features, properties, attributes, relationships and/or methods whichprovide similar capabilities and functionalities.

It will be readily understood that the features of exemplary embodimentsas generally described and illustrated in the Figures can be arrangedand designed in a wide array of different configurations. That is,features, structures and/or characteristics of embodiments orarrangements described herein may be combined in any suitable manner inone or other embodiments or arrangements. Thus the detailed descriptionof the exemplary embodiments of apparatus, methods and articles asrepresented in the Figures is not intended to limit the scope of theembodiments as claimed, but is merely representative of selectedexemplary embodiments that implement the principles described herein.

In the foregoing description certain terms have been used to describeexample arrangements for purposes of brevity, clarity and understanding.For example certain terms such as “upward”, “downward”, “higher”,“lower”, “left”, “right”, “outer”, “inner”, “front”, “rear”, “top”, and“bottom” may have been used. However, no unnecessary limitations are tobe implied therefrom because such terms have been used for descriptivepurposes and are intended to be broadly construed. The terms shall notbe construed as limitations on the scope of the claims hereof. Moreover,the descriptions and illustrations herein are by way of examples and theinventive teachings are not limited to the specific details that havebeen shown and described.

The exemplary structures and arrangements along with the methods ofpreparing and using such structures and arrangements achieves at leastone of the above stated objectives, eliminates difficulties encounteredin the use of prior devices and systems, solves problems and attains thedesirable results described herein.

In the following claims, any feature described as a means for performinga function shall be construed as encompassing any means known to thoseskilled in the art to be capable of performing the recited function andshall not be deemed to be limited to the particular means used forperforming the function in the foregoing description or mere equivalentsthereof.

Having described the features, discoveries and principles of theexemplary embodiments, the manner in which they are constructed andoperated and the advantages and useful results attained, the new anduseful structures, devices, elements, arrangements, parts, combinations,systems, equipment, operations, methods, processes and relationships areset forth in the appended claims.

We claim:
 1. Apparatus comprising: a fluid actuated clutch, wherein theclutch is configured to selectively engage and disengage a rotatabledriver and a rotatable load, wherein the clutch includes a disc housing,wherein the disc housing is configured to be in fixed operativerotational connection with one of the driver or the load, a hub, whereinthe hub is configured to be in fixed operative rotational connectionwith the other of the driver or the load, wherein the hub extends inconcentric relation relative to a central axis and radially inward ofthe disc housing, wherein the hub and the disc housing are relativelyrotationally movable about the axis, a disc pack, wherein the disc packincludes at least two axially spaced clutch discs, wherein each clutchdisc is in operatively engaged rotational connection with the dischousing, wherein each clutch disc is relatively axially movable relativeto the hub and the disc housing, at least one separator disc, whereinthe at least one separator disc is axially intermediate of animmediately axially adjacent pair of clutch discs, wherein eachseparator disc is in operatively engaged rotational connection with thehub, and wherein each separator disc is axially movable relative to thedisc housing and the hub, a cylinder, wherein the cylinder includes ahousing, a piston, wherein the piston is axially movable in operativelysupported relation with the housing, wherein the piston and the housingbound a cavity, wherein the cavity has a volume that is variableresponsive to delivery and release of pressurized fluid to and from thecavity, wherein the piston is in operative connection with the discpack, wherein the piston is selectively axially movable in a first axialdirection responsive to delivery of pressurized fluid to the cavity andis operative to apply axial compressive force to the plurality of clutchdiscs and the at least one separator disc, whereby the disc housing andthe hub rotate in engaged relation, and wherein the piston isselectively axially movable in a second axial direction opposed of thefirst axial direction, responsive to release of pressurized fluid fromthe cavity, whereby the disc housing and the hub are enabled toindependently rotate, wherein the disc housing includes an innercontinuous annular housing ring, wherein the inner annular housing ringincludes an inner annular splined surface, wherein the inner annularsplined surface includes a plurality of angularly spaced radially inwarddirected axially elongated ring splines, wherein the inward directedring splines are in engagement with corresponding radially outwarddirected clutch disc splines which extend at a radially outer peripheryof each of the clutch discs, a plurality of radially outward directedangularly spaced inner ring projections, wherein the inner ringprojections radially outwardly overlie the inner annular splinedsurface, wherein in axially transverse cross-section each inner ringprojection is bounded by a pair of angularly spaced, radially extendinginner ring projection sidewalls and an inner ring projection top wall,wherein the inner ring projection top wall radially outwardly bounds therespective inner ring projection and extends transversely between theinner ring projection sidewalls, an outer annular housing ring, whereinthe outer annular housing ring is concentric with the inner annularhousing ring, radially outwardly overlies at least a portion of theinner annular housing ring and is rotationally movable relative to theinner annular housing ring, wherein the outer annular housing ringincludes a plurality of at least one of angularly spaced engagementprojections and engagement openings, wherein the at least one of theengagement projections and engagement openings is configured toreleasably operatively engage the outer annular housing ring and arotatable member of the one of the driver or the load, a plurality ofradially inward extending angularly spaced outer ring projections,wherein in axially transverse cross-section each of the outer ringprojections is bounded by a pair of angularly spaced radially extendingouter ring projection sidewalls, and an outer ring projection bottomwall, wherein the outer ring projection bottom wall radially inwardlybounds the respective outer ring projection and extends transverselybetween the outer ring projection sidewalls, wherein each outer ringprojection extends intermediate of an immediately adjacent pair of innerring projections such that each outer ring projection sidewall is inangularly disposed facing relation with an immediately adjacent innerring projection sidewall, a plurality of resilient bodies, wherein atleast one resilient body extends angularly between each immediatelyadjacent outer ring projection sidewall and inner ring projectionsidewall, wherein each resilient body biasingly maintains a respectiveimmediately adjacent outer ring projection sidewall and inner ringprojection sidewall angularly separated.
 2. The apparatus according toclaim 1 wherein the resilient bodies comprise at least one of coilcompression springs, resilient blocks, or resilient tubes.
 3. Theapparatus according to claim 2 wherein each resilient body comprises acoil compression spring, wherein at least one of an immediately adjacentinner ring projection sidewall and outer ring projection sidewallincludes a nesting recess, wherein the nesting recess extendsperpendicular to the radial direction, wherein a respective compressionspring extends in the respective nesting recess.
 4. The apparatusaccording to claim 2 wherein each resilient body comprises the resilientblock, wherein the resilient block in axially transverse cross-sectionincludes a pair of angularly disposed radially extending blocksidewalls, wherein one radially extending block sidewall of eachresilient body is in abutting engagement with one of an immediatelyangularly adjacent inner ring projection sidewall and outer ringprojection sidewall, and the other radially extending block sidewall isin abutting engagement with the other of the immediately angularlyadjacent inner ring projection sidewall and outer ring projectionsidewall.
 5. The apparatus according to claim 2 wherein each resilientbody comprises the resilient tube, wherein each resilient tube extendsalong a tube axis parallel to the axis, wherein each immediatelyangularly adjacent inner ring projection sidewall and outer ringprojection sidewall includes in axially transverse cross-section, asemicircular recess, wherein each semicircular recess is elongated in adirection parallel to the axis, and wherein one tube extends in eachimmediately angularly adjacent pair of semicircular recesses.
 6. Theapparatus according to claim 2 wherein the outer annular housing ringextends in radially outward overlying relation of each of the pluralityof resilient bodies.
 7. The apparatus according to claim 6 wherein theouter annular housing ring extends in radially outward overlyingrelation of each inner ring projection top wall of each inner ringprojection.
 8. The apparatus according to claim 2 wherein the innerhousing ring further includes in axially transverse cross-section aplurality of arcuate outer segment surfaces, wherein each arcuate outersegment surface extends intermediate and radially inward of immediatelyangularly adjacent inner ring projections, a plurality of resilientspacers, wherein each resilient spacer extends radially intermediate ofeach arcuate outer segment surface and an immediately radially adjacentouter ring projection bottom wall.
 9. The apparatus according to claim 8wherein each resilient spacer comprises one of a radially inward portionof the resilient body, or a resilient pad that is positioned between arespective arcuate outer segment surface and a respective outer ringprojection bottom wall.
 10. The apparatus according to claim 9 whereinthe hub includes an annular splined outer hub surface, wherein the atleast one separator disc includes a central disc piece, wherein thecentral disc piece includes an annular splined separator inner surface,wherein the splined separator inner surface is in engaged relation withthe splined hub outer surface, a pair of outer disc pieces, wherein oneouter disc piece extends on an opposed axial side of the central discpiece from another of the pair of outer disc pieces, wherein the centraldisc piece is rotationally movable relative to both of the outer discpieces, at least one deformable resilient component, wherein the atleast one deformable resilient component is operatively positionedintermediate of at least one of the outer disc pieces and the centraldisc piece, wherein the at least one deformable resilient component isoperative to resist relative rotational movement of at least one outerdisc piece and the central disc piece.
 11. The apparatus according toclaim 10 wherein the at least one deformable resilient componentcomprises one of a plurality of angularly spaced annularly arrangedseparator compression springs, or a pair of planar elastic discs,wherein one elastic disc extends on each axial side of the central discpiece and axially between an outer disc piece and the central discpiece.
 12. The apparatus according to claim 11 wherein the at least onedeformable resilient component comprises the plurality of angularlyspaced, annularly arranged separator compression springs, wherein inaxial transverse cross-section the central disc piece comprises aplurality of angularly spaced, radially outward extending posts, andwherein each of the outer disc pieces include aligned angularly spacedradially inward extending projections, wherein the projections extendangularly intermediate of each immediately angularly adjacent pair ofposts, wherein a separator compression spring extends between each postand each projection.
 13. The apparatus according to claim 11 wherein theat least one resilient component comprises the pair of planar elasticdiscs, wherein the central disc piece includes a central disc plateportion including opposed central disc plate planar faces, wherein eachcentral disc plate planar face is engaged with a respective one planarelastic disc.
 14. The apparatus according to claim 1 wherein the hubincludes an annular splined outer hub surface, wherein the at least oneseparator disc includes a central disc piece, wherein the central discpiece includes an annular splined separator inner surface, wherein thesplined separator inner surface is in engaged relation with the splinedhub outer surface, a pair of outer disc pieces, wherein one outer discpiece extends on an opposed axial side of the central disc piece fromanother of the pair of outer disc pieces, wherein the central disc pieceis rotationally movable relative to both of the outer disc pieces, atleast one deformable resilient component, wherein the at least onedeformable resilient component is operatively positioned operativelyintermediate of at least one of the outer disc pieces and the centraldisc piece, wherein the at least one deformable resilient component isoperative to resist relative rotational movement of the at least oneouter disc piece and the central disc piece.
 15. Apparatus comprising: afluid actuated clutch, wherein the clutch is configured to selectivelyengage and disengage a rotatable driver and a rotatable load, whereinthe clutch includes a disc housing, wherein the disc housing isconfigured to be in fixed operative rotational connection with one ofthe driver or the load, a hub, wherein the hub is configured to be infixed operative rotational connection with the other of the driver orthe load, wherein the hub extends in concentric relation relative to acentral axis and radially inward of the disc housing, wherein the huband the disc housing are relatively rotationally movable about the axis,a disc pack, wherein the disc pack includes at least two axially spacedclutch discs, wherein each clutch disc is in operatively engagedrotational connection with the disc housing, wherein each clutch disc isrelatively axially movable relative to the hub and the disc housing, atleast one separator disc, wherein the at least one separator disc isaxially intermediate of an immediately axially adjacent pair of clutchdiscs, wherein each separator disc is in operatively engaged rotationalconnection with the hub, and wherein each separator disc is axiallymovable relative to the disc housing and the hub, a cylinder, whereinthe cylinder includes a housing, a piston, wherein the piston is axiallymovable in operatively supported relation with the housing, wherein thepiston and the housing bound a cavity, wherein the cavity has a volumethat is variable responsive to delivery and release of pressurized fluidto and from the cavity, wherein the piston is in operative connectionwith the disc pack, wherein the piston is selectively axially movable ina first axial direction responsive to delivery of pressurized fluid tothe cavity and is operative to apply axial compressive force to theplurality of clutch discs and the at least one separator disc, wherebythe disc housing and the hub rotate in engaged relation, wherein thepiston is selectively axially movable in a second axial directionopposed of the first axial direction, responsive to release ofpressurized fluid from the cavity, whereby the disc housing and the hubare enabled to independently rotate, wherein the hub includes an annularsplined outer hub surface, wherein the at least one separator discincludes a central disc piece, wherein the central disc piece includesan annular splined separator inner surface, wherein the splinedseparator inner surface is in engaged relation with the splined hubouter surface, a pair of outer disc pieces, wherein each outer discpiece of the pair extends axially intermediate of an immediately axiallyadjacent pair of clutch discs, wherein one outer disc piece extends onan opposed axial side of the central disc piece from another of the pairof outer disc pieces, wherein the central disc piece is rotationallymovable relative to both of the outer disc pieces, at least onedeformable resilient component, wherein the at least one deformableresilient component is operatively positioned intermediate of at leastone of the outer disc pieces and the central disc piece, wherein the atleast one deformable resilient component is operative to resist relativerotational movement of at least one outer disc piece and the centraldisc piece.
 16. The apparatus according to claim 15 wherein the at leastone deformable resilient component comprises one of a plurality ofangularly spaced annularly arranged separator compression springs, or apair of planar elastic discs, wherein one elastic disc extends on eachaxial side of the central disc piece and axially between an outer discpiece and the central disc piece.
 17. The apparatus according to claim16 wherein the at least one deformable resilient component comprises theplurality of angularly spaced, annularly arranged separator compressionsprings, wherein in axial transverse cross-section the central discpiece comprises a plurality of angularly spaced, radially outwardextending posts, and wherein each of the outer disc pieces includealigned angularly spaced radially inward extending projections, whereinthe projections extend angularly intermediate of each immediatelyangularly adjacent pair of posts, wherein a separator compression springextends between each post and each projection.
 18. The apparatusaccording to claim 16 wherein the at least one deformable resilientcomponent comprises the pair of planar elastic discs, wherein thecentral disc piece includes a central disc plate portion includingopposed central disc plate planar faces, wherein each central disc plateplanar face is engaged with a respective one planar elastic disc. 19.The apparatus according to claim 16 wherein the disc housing includes aninner annular housing ring, wherein the inner annular housing ringincludes an inner annular splined surface, wherein the inner annularsplined surface includes a plurality of angularly spaced radially inwarddirected axially elongated ring splines, wherein the inward directedring splines are in engagement with corresponding radially outwarddirected clutch disc splines which extend at a radially outer peripheryof each of the clutch discs, a plurality of radially outward directedangularly spaced inner ring projections, wherein the inner ringprojections radially outwardly overlie the inner annular splinedsurface, wherein in axially transverse cross-section each inner ringprojection is bounded by a pair of angularly spaced, radially extendinginner ring projection sidewalls and an inner ring projection top wall,wherein the inner ring projection top wall radially outwardly bounds therespective inner ring projection and extends transversely between theinner ring projection sidewalls, an outer annular housing ring, whereinthe outer annular housing ring is concentric with the inner annularhousing ring, radially outwardly overlies at least a portion of theinner annular housing ring and is rotationally movable about the axisrelative to the inner annular housing ring, wherein the outer annularhousing ring includes a plurality of at least one of angularly spacedengagement projections and engagement openings, wherein the at least oneof the engagement projections and engagement openings is configured toreleasably engage the outer annular housing ring and a rotatable memberof the one of the driver or the load, a plurality of radially extendingangularly spaced outer ring projections, wherein in axially transversecross-section each of the outer ring projections is bounded by a pair ofangularly spaced radially extending outer ring projection sidewalls, andan outer ring projection bottom wall, wherein the outer ring projectionbottom wall radially inwardly bounds the respective outer ringprojection and extends transversely between the outer ring projectionsidewalls, wherein each outer ring projection extends intermediate of animmediately adjacent pair of inner ring projections such that each outerring projection sidewall is in angularly disposed facing relation withan immediate adjacent inner ring projection sidewall, a plurality ofresilient bodies, wherein at least one resilient body extends betweeneach immediately adjacent outer ring projection sidewall and inner ringprojection sidewall.
 20. The apparatus according to claim 16 wherein thedisc housing includes an inner annular housing ring, wherein the innerannular housing ring includes an inner annular splined surface, whereinthe inner annular splined surface includes a plurality of angularlyspaced radially inward directed axially elongated ring splines, whereinthe inward directed ring splines are in engagement with correspondingradially outward directed clutch disc splines which extend at a radiallyouter periphery of each of the clutch discs, a plurality of radiallyoutward directed angularly spaced inner ring projections, wherein theinner ring projections radially outwardly overlie at least a portion ofthe inner annular splined surface, wherein in axially transversecross-section each inner ring projection is bounded by a pair ofangularly spaced, radially extending inner ring projection sidewalls andan inner ring projection top wall, wherein the inner ring projection topwall radially outwardly bounds the respective inner ring projection andextends transversely between the inner ring projection sidewalls, anouter annular housing ring, wherein the outer annular housing ring isconcentric with the inner annular housing ring, radially outwardlyoverlies the inner annular housing ring and is rotationally movableabout the axis relative to the inner annular housing ring, wherein theouter annular housing ring includes a plurality of at least one ofangularly spaced engagement projections and engagement openings, whereinthe at least one of the engagement projections and engagement openingsis configured to releasably engage the outer annular housing ring and arotatable member of the one of the driver or the load, a plurality ofradially extending angularly spaced outer ring projections, wherein inaxially transverse cross-section each of the outer ring projections isbounded by a pair of angularly spaced radially extending outer ringprojection sidewalls, and an outer ring projection bottom wall, whereinthe outer ring projection bottom wall radially inwardly bounds therespective outer ring projection and extends transversely between theouter ring projection sidewalls, wherein each outer ring projectionextends intermediate of an immediately adjacent pair of inner ringprojections such that each outer ring projection sidewall is inangularly disposed facing relation with an immediate adjacent inner ringprojection sidewall, a plurality of deformable resilient bodies, whereinat least one deformable resilient body extends between each immediatelyadjacent outer ring projection sidewall and inner ring projectionsidewall.
 21. Apparatus comprising: a fluid actuated clutch, wherein theclutch is configured to selectively engage and disengage a rotatabledriver and a rotatable load, wherein the clutch includes a disc housing,wherein the disc housing is configured to be in fixed operativerotational connection with one of the driver or the load, a hub, whereinthe hub is configured to be in fixed operative rotational connectionwith the other of the driver or the load, wherein the hub extends inconcentric relation relative to a central axis and radially inward ofthe disc housing, wherein the hub and the disc housing are relativelyrotationally movable about the axis, a disc pack, wherein the disc packincludes at least two axially spaced clutch discs, wherein each clutchdisc is in operatively engaged rotational connection with the dischousing, wherein each clutch disc is relatively axially movable relativeto the hub and the disc housing, at least one separator disc, whereinthe at least one separator disc is axially intermediate of animmediately axially adjacent pair of clutch discs, wherein eachseparator disc is in operatively engaged rotational connection with thehub, and wherein each separator disc is axially movable relative to thedisc housing and the hub, a cylinder, wherein the cylinder includes ahousing, a piston, wherein the piston is axially movable in operativelysupported relation with the housing, wherein the piston and the housingbound a cavity, wherein the cavity has a volume that is variableresponsive to delivery and release of pressurized fluid to and from thecavity, wherein the piston is in operative connection with the discpack, wherein the piston is selectively axially movable in a first axialdirection responsive to delivery of pressurized fluid to the cavity andis operative to apply axial compressive force to the plurality of clutchdiscs and the at least one separator disc, whereby the disc housing andthe hub rotate in engaged relation, and wherein the piston isselectively axially movable in a second axial direction opposed of thefirst axial direction, responsive to release of pressurized fluid fromthe cavity, whereby the disc housing and the hub are enabled toindependently rotate, wherein the disc housing includes an inner annularhousing ring, wherein the inner annular housing ring includes an innerannular splined surface, wherein the inner annular splined surfaceincludes a plurality of angularly spaced radially inward directedaxially elongated ring splines, wherein the inward directed ring splinesare in engagement with corresponding radially outward directed clutchdisc splines which extend at a radially outer periphery of each of theclutch discs, a plurality of radially outward directed, angularly spacedinner ring projections, wherein each of the inner ring projectionsextend radially outwardly relative to the axis and the inner annularsplined surface, wherein in axially transverse cross-section each innerring projection is bounded by a pair of angularly spaced, radiallyextending inner ring projection sidewalls and an inner ring projectiontop wall, wherein the inner ring projection top wall extends between theinner ring projection sidewalls, an outer annular housing ring, whereinthe outer annular housing ring is concentric with the inner annularhousing ring, radially outwardly overlies at least a portion of theinner annular housing ring and is rotationally movable relative to theinner annular housing ring, wherein the outer annular housing ringincludes at least one engagement projection or engagement opening,wherein the at least one engagement projection or engagement opening isconfigured to releasably operatively engage the outer annular housingring and a rotatable member of the one of the driver or the load, aplurality of radially inward directed, angularly spaced outer ringprojections, wherein each of the outer ring projections extend radiallyinwardly relative to the axis, wherein in axially transversecross-section each of the outer ring projections is bounded by a pair ofangularly spaced, radially extending outer ring projection sidewalls,and an outer ring projection bottom wall, wherein the outer ringprojection bottom wall extends between the outer ring projectionsidewalls, wherein each outer ring projection extends intermediate of animmediately adjacent pair of inner ring projections such that each outerring projection sidewall is in angularly disposed facing relation withan immediately adjacent inner ring projection sidewall, a plurality ofresilient bodies, wherein in axially transverse cross-section at leastone resilient body extends angularly intermediate of each immediatelyadjacent outer ring projection sidewall and inner ring projectionsidewall.
 22. The apparatus according to claim 21 wherein the hubincludes an annular splined outer hub surface, wherein the at least oneseparator disc includes a central disc piece, wherein the central discpiece includes an annular splined separator inner surface, wherein thesplined separator inner surface is in axially moveable engaged relationwith the splined hub outer surface, at least one outer disc piece,wherein the central disc piece is rotationally movable relative to theat least one outer disc piece, at least one deformable resilientcomponent, wherein the at least one deformable resilient component isoperatively positioned intermediate of the at least one of the outerdisc piece and the central disc piece, wherein the at least onedeformable resilient component is operative to resist relativerotational movement of the at least one outer disc piece and the centraldisc piece.
 23. Apparatus comprising: a fluid actuated clutch, whereinthe clutch is configured to selectively engage and disengage a rotatabledriver and a rotatable load, wherein the clutch includes a disc housing,wherein the disc housing is configured to be in fixed operativerotational connection with one of the driver or the load, a hub, whereinthe hub is configured to be in fixed operative rotational connectionwith the other of the driver or the load, wherein the hub extends inconcentric relation relative to a central axis and radially inward ofthe disc housing, wherein the hub and the disc housing are relativelyrotationally movable about the axis, a disc pack, wherein the disc packincludes at least two axially spaced clutch discs, wherein each clutchdisc is in operatively engaged rotational connection with the dischousing, wherein each clutch disc is relatively axially movable relativeto the hub and the disc housing, at least one separator disc, whereinthe at least one separator disc is axially intermediate of animmediately axially adjacent pair of clutch discs, wherein eachseparator disc is in operatively engaged rotational connection with thehub, and wherein each separator disc is axially movable relative to thedisc housing and the hub, a cylinder, wherein the cylinder includes ahousing, a piston, wherein the piston is axially movable in operativelysupported relation with the housing, wherein the piston and the housingbound a cavity, wherein the cavity has a volume that is variableresponsive to delivery and release of pressurized fluid to and from thecavity, wherein the piston is in operative connection with the discpack, wherein the piston is selectively axially movable in a first axialdirection responsive to delivery of pressurized fluid to the cavity andis operative to apply axial compressive force to the plurality of clutchdiscs and the at least one separator disc, whereby the disc housing andthe hub rotate in engaged relation, wherein the piston is selectivelyaxially movable in a second axial direction opposed of the first axialdirection, responsive to release of pressurized fluid from the cavity,whereby the disc housing and the hub are enabled to independentlyrotate, wherein the hub includes an annular splined outer hub surface,wherein the at least one separator disc includes a central disc piece,wherein the central disc piece includes an annular splined separatorinner surface, wherein the splined separator inner surface is in axiallymovable engaged relation with the splined hub outer surface, at leastone outer disc piece, wherein the at least one outer disc piece extendsaxially intermediate of an immediately axially adjacent pair of clutchdiscs, wherein the central disc piece is rotationally movable relativeto the at least one outer disc piece, at least one deformable resilientcomponent, wherein the at least one deformable resilient component isoperatively positioned intermediate of the at least one outer disc pieceand the central disc piece, wherein the at least one deformableresilient component is operative to resist relative rotational movementof the at least one outer disc piece and the central disc piece.
 24. Theapparatus according to claim 23 wherein the disc housing includes aninner annular housing ring, wherein the inner annular housing ringincludes an inner annular splined surface, wherein the inner annularsplined surface includes a plurality of angularly spaced radially inwarddirected axially elongated ring splines, wherein the inward directedring splines are in engagement with corresponding radially outwarddirected clutch disc splines which extend at a radially outer peripheryof each of the clutch discs, a plurality of radially outward directed,angularly spaced inner ring projections, wherein each of the inner ringprojections extend radially outwardly relative to the axis and the innerannular splined surface, wherein in axially transverse cross-sectioneach inner ring projection is bounded by a pair of angularly spaced,radially extending inner ring projection sidewalls and an inner ringprojection top wall, wherein the inner ring projection top wall extendsbetween the inner ring projection sidewalls, an outer annular housingring, wherein the outer annular housing ring is concentric with theinner annular housing ring, radially outwardly overlies at least aportion of the inner annular housing ring and is rotationally movableabout the axis relative to the inner annular housing ring, wherein theouter annular housing ring includes at least one engagement projectionor engagement opening, wherein the at least one engagement projection orengagement opening is configured to releasably operatively engage theouter annular housing ring and a rotatable member of the one of thedriver or the load, a plurality of radially inward directed, angularlyspaced outer ring projections, when each of the outer ring projectionsextend radially inwardly relative to the axis, wherein in axiallytransverse cross-section each of the outer ring projections is boundedby a pair of angularly spaced, radially extending outer ring projectionsidewalls, and an outer ring projection bottom wall, wherein the outerring projection bottom wall extends between the outer ring projectionsidewalls, wherein each outer ring projection extends intermediate of animmediately adjacent pair of inner ring projections such that each outerring projection sidewall is in angularly disposed facing relation withan immediately adjacent inner ring projection sidewall, a plurality ofresilient bodies, wherein in axially transverse cross-section at leastone resilient body extends angularly intermediate of each immediatelyadjacent outer ring projection sidewall and inner ring projectionsidewall.